Refrigeration cycle apparatus

ABSTRACT

A refrigeration cycle apparatus efficiently performs a cooling operation and a heating operation using a low-pressure refrigerant and a high-pressure refrigerant. A refrigeration cycle apparatus using a first refrigerant having 1 MPa or less at 30° C. and a second refrigerant having 1.5 MPa or more at 30° C. performs a heating operation by performing a two-stage refrigeration cycle including a use-side refrigeration cycle using the first refrigerant and a heat-source-side refrigeration cycle using the second refrigerant, and performs a cooling operation by performing a single-stage refrigeration cycle using the first refrigerant.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a Continuation of PCT International Application No. PCT/JP2022/016796, filed on Mar. 31, 2022, which claims priority under 35 U.S.C. § 119(a) to Patent Application No. JP 2021-061278, filed in Japan on Mar. 31, 2021, all of which are hereby expressly incorporated by reference into the present application.

TECHNICAL FIELD

The present disclosure relates to a refrigeration cycle apparatus.

BACKGROUND ART

To date, refrigeration cycle apparatuses have been proposed that use refrigerants with low global warming potential (GWP), taking into account the global environment.

For example, in a refrigeration cycle apparatus described in PTL 1 (Japanese Unexamined Patent Application Publication No. 2015-197254), it is proposed to fill a refrigerant circuit with a working fluid having a GWP equal to or less than a predetermined value.

SUMMARY

A refrigeration cycle apparatus according to a first aspect performs a heating operation by performing a two-stage refrigeration cycle, the two-stage refrigeration cycle including a use-side refrigeration cycle using a first refrigerant and a heat-source-side refrigeration cycle using a 20 second refrigerant. The first refrigerant has 1 MPa or less at 30° C. The second refrigerant has 1.5 MPa or more at 30° C. The refrigeration cycle apparatus performs a cooling operation by performing a single-stage refrigeration cycle using the first refrigerant.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is an overall configuration diagram of a refrigeration cycle apparatus according to a first embodiment.

FIG. 2 is a functional block configuration diagram of the refrigeration cycle apparatus according to the first embodiment.

FIG. 3 is a diagram illustrating how a refrigerant flows during a cooling operation according to the first embodiment.

FIG. 4 is a diagram illustrating how a refrigerant flows during a heating operation according to the first embodiment.

FIG. 5 is an overall configuration diagram of a refrigeration cycle apparatus according to a second embodiment.

FIG. 6 is a functional block configuration diagram of the refrigeration cycle apparatus according to the second embodiment.

FIG. 7 is a diagram illustrating how a refrigerant flows during a cooling operation according to the second embodiment.

FIG. 8 is a diagram illustrating how a refrigerant flows during a heating operation according to the second embodiment.

FIG. 9 is an overall configuration diagram of a refrigeration cycle apparatus according to a third embodiment.

FIG. 10 is a functional block configuration diagram of the refrigeration cycle apparatus according to the third embodiment.

FIG. 11 is a diagram illustrating how a refrigerant flows during a cooling operation according to the third embodiment.

FIG. 12 is a diagram illustrating how a refrigerant flows during a heating operation according to the third embodiment.

FIG. 13 is an overall configuration diagram of a refrigeration cycle apparatus according to a fourth embodiment.

FIG. 14 is a functional block configuration diagram of the refrigeration cycle apparatus according to the fourth embodiment.

FIG. 15 is a diagram illustrating how a refrigerant flows during a cooling operation according to the fourth embodiment.

FIG. 16 is a diagram illustrating how a refrigerant flows during a heating operation according to the fourth embodiment.

DESCRIPTION OF EMBODIMENTS (1) First Embodiment

FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus 1 according to a first embodiment. FIG. 2 is a functional block configuration diagram of the refrigeration cycle apparatus 1 according to the first embodiment.

The refrigeration cycle apparatus 1 is an apparatus used to process a heat load through a vapor-compression refrigeration cycle operation. The refrigeration cycle apparatus 1 includes a heat-load circuit 90, a refrigerant circuit 10, an outdoor fan 9, and a controller 7.

The heat load to be processed by the refrigeration cycle apparatus 1 is not limited, and a fluid such as air, water, or brine may be subjected to heat exchange. In the refrigeration cycle apparatus 1 according to the present embodiment, water flowing through the heat-load circuit 90 is supplied to a heat-load heat exchanger 91, and the heat load in the heat-load heat exchanger 91 is processed. The heat-load circuit 90 is a circuit in which water serving as a heat medium circulates, and includes the heat-load heat exchanger 91, a pump 92, and a use heat exchanger 13 shared with the refrigerant circuit 10. The pump 92 is driven and controlled by the controller 7, which will be described below, to circulate the water through the heat-load circuit 90. In the heat-load circuit 90, the water flows through a heat-load flow path 13 b included in the use heat exchanger 13. As described below, the use heat exchanger 13 includes a first use flow path 13 a through which a first refrigerant flowing through the refrigerant circuit 10 passes. The water flowing through the heat-load flow path 13 b of the use heat exchanger 13 exchanges heat with the first refrigerant flowing through the first use flow path 13 a. As a result, the water is cooled during a cooling operation and is heated during a heating operation.

The refrigerant circuit 10 includes a first compressor 11, a second compressor 21, a first switching mechanism 12, the use heat exchanger 13 shared with the heat-load circuit 90, a first expansion valve 15, a second expansion valve 16, a third expansion valve 14, a cascade heat exchanger 17, an outdoor heat exchanger 18, a first on-off valve 41, and a second on-off valve 42.

The refrigerant circuit 10 is filled with the first refrigerant, which is a low-pressure refrigerant, and a second refrigerant, which is a high-pressure refrigerant, as refrigerants in a substantially separated state. The first refrigerant is a refrigerant having 1 MPa or less at 30° C., and is a refrigerant including, for example, at least one of R1234yf or R1234ze. The first refrigerant may include only R1234yf or may include only R1234ze. The second refrigerant is a refrigerant having 1.5 MPa or more at 30° C. For example, the second refrigerant may include carbon dioxide, or may include only carbon dioxide.

The first compressor 11 is a positive-displacement compressor to be driven by a compressor motor. The compressor motor is driven by electric power supplied via an inverter device. The first compressor 11 has an operating capacity that is changeable by varying a drive frequency that is the number of rotations of the compressor motor. A discharge side of the first compressor 11 is connected to a first port of the first switching mechanism 12. A suction side of the first compressor 11 is connected to a second port of the first switching mechanism 12 and a gas refrigerant side of a first cascade flow path 17 a of the cascade heat exchanger 17.

The first switching mechanism 12 switches between a state in which the discharge side of the first compressor 11 is connected to a gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 and the suction side of the first compressor 11 is connected to the first on-off valve 41 and the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17 and a state in which the discharge side of the first compressor 11 is connected to the first on-off valve 41 and the suction side of the first compressor 11 is connected to the gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 and the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17. In the present embodiment, the first switching mechanism 12 is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port is connected to the discharge side of the first compressor 11. The second port is connected to the suction side of the first compressor 11 and the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17. The third port is connected to the gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13. The fourth port is connected to the first on-off valve 41.

The gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 through which the first refrigerant flowing through the refrigerant circuit 10 passes is connected to the first switching mechanism 12. A liquid refrigerant side of the first use flow path 13 a is connected to a branch point A included in the refrigerant circuit 10.

At the branch point A, a flow path extending from the liquid refrigerant side of the first use flow path 13 a, a flow path extending to the side of the first expansion valve 15 opposite to the cascade heat exchanger 17 side, and a flow path extending from the third expansion valve 14 are connected.

The first expansion valve 15 is configured as an electronic expansion valve that is adjustable in valve opening degree. In the refrigerant circuit 10, the first expansion valve 15 is disposed between the branch point A and a liquid refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17.

The third expansion valve 14 is configured as an electronic expansion valve that is adjustable in valve opening degree. In the refrigerant circuit 10, the third expansion valve 14 is disposed at a certain point in a flow path connecting the branch point A and a branch point B.

At the branch point B, a flow path extending from the third expansion valve 14, a flow path extending from the second expansion valve 16, and a flow path extending from a liquid refrigerant side of the outdoor heat exchanger 18 are connected.

The second expansion valve 16 is configured as an electronic expansion valve that is adjustable in valve opening degree. In the refrigerant circuit 10, the second expansion valve 16 is disposed between the branch point B and a liquid refrigerant side of a second cascade flow path 17 b of the cascade heat exchanger 17.

The cascade heat exchanger 17 is a cascade heat exchanger that includes the first cascade flow path 17 a through which one of the first refrigerant and the second refrigerant passes and the second cascade flow path 17 b through which the other of the first refrigerant and the second refrigerant passes, and that exchanges heat between the first refrigerant and the second refrigerant. In the cascade heat exchanger 17, the first cascade flow path 17 a and the second cascade flow path 17 b are independent of each other, and the first refrigerant and the second refrigerant do not mix with each other in the cascade heat exchanger 17. The gas refrigerant side of the first cascade flow path 17 a is connected to the suction side of the first compressor 11. The liquid refrigerant side of the first cascade flow path 17 a is connected to a flow path extending from the first expansion valve 15. A gas refrigerant side of the second cascade flow path 17 b is connected to a discharge side of the second compressor 21. The liquid refrigerant side of the second cascade flow path 17 b is connected to a flow path extending from the second expansion valve 16.

The outdoor heat exchanger 18 includes a plurality of heat transfer tubes and a plurality of fins joined to the plurality of heat transfer tubes. In the present embodiment, the outdoor heat exchanger 18 is arranged outdoors. A refrigerant flowing through the outdoor heat exchanger 18 exchanges heat with air sent to the outdoor heat exchanger 18.

The outdoor fan 9 generates an air flow of outdoor air passing through the outdoor heat exchanger 18.

A branch point C is connected to a flow path extending from a gas refrigerant side of the outdoor heat exchanger 18, a flow path extending from the first on-off valve 41, and a flow path extending from the second on-off valve 42.

The first on-off valve 41 is disposed at a certain point in a flow path connecting the branch point C and the fourth port of the first switching mechanism 12.

The second on-off valve 42 is disposed at a certain point in a flow path connecting the branch point C and a suction side of the second compressor 21.

The second compressor 21 is a positive-displacement compressor to be driven by a compressor motor. The compressor motor is driven by electric power supplied via an inverter device. The second compressor 21 has an operating capacity that is changeable by varying a drive frequency that is the number of rotations of the compressor motor. The discharge side of the second compressor 21 is connected to the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17. The suction side of the second compressor 21 is connected to a flow path extending from the second on-off valve 42.

The controller 7 controls the operation of the devices included in the heat-load circuit 90 and the refrigerant circuit 10. Specifically, the controller 7 includes a processor serving as a CPU provided for performing control, a memory, and the like.

In the refrigeration cycle apparatus 1 described above, the controller 7 controls the devices to execute a refrigeration cycle, thereby performing a cooling operation for processing a cooling load in the heat-load heat exchanger 91, a heating operation for processing a heating load in the heat-load heat exchanger 91, a cooling-to-heating transition operation, and a heating-to-cooling transition operation.

(1-1) Cooling Operation

During the cooling operation, as illustrated in FIG. 3 , the second refrigerant is confined in a flow path (flow path indicated by a dotted line) from the second on-off valve 42 to the second expansion valve 16 via the second compressor 21 and the second cascade flow path 17 b of the cascade heat exchanger 17, and the first refrigerant is circulated through the first compressor 11, the outdoor heat exchanger 18, the third expansion valve 14, and the use heat exchanger 13. As a result, a single-stage refrigeration cycle is performed. The single-stage refrigeration cycle is performed using the first refrigerant by causing the use heat exchanger 13 to function as an evaporator of the first refrigerant and the outdoor heat exchanger 18 to function as a condenser of the first refrigerant. In FIG. 3 , a single-headed arrow indicates a flow path through which the first refrigerant flows.

Specifically, the second on-off valve 42 and the second expansion valve 16 are controlled to be in a fully closed state to confine the second refrigerant in the flow path from the second on-off valve 42 to the second expansion valve 16. Further, a connection state of the first switching mechanism 12 is switched to a connection state indicated by solid lines in FIG. 3 , the pump 92, the first compressor 11, and the outdoor fan 9 are driven, the first on-off valve 41 is controlled to be in an open state, the first expansion valve 15 is controlled to be in a fully closed state, and the second compressor 21 is stopped. Further, the valve opening degree of the third expansion valve 14 is controlled such that the degree of superheating of the first refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition.

Accordingly, the first refrigerant discharged from the first compressor 11 is sent to the outdoor heat exchanger 18 via the first switching mechanism 12 and the first on-off valve 41. The first refrigerant sent to the outdoor heat exchanger 18 is condensed by heat exchange with the outdoor air supplied by the outdoor fan 9. The first refrigerant having passed through the outdoor heat exchanger 18 passes through the branch point B and is then decompressed in the third expansion valve 14. After that, the first refrigerant passes through the branch point A and is sent to the first use flow path 13 a of the use heat exchanger 13. The first refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is evaporated by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water cooled by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the cooling load. The first refrigerant evaporated in the first use flow path 13 a of the use heat exchanger 13 is sucked into the first compressor 11 via the first switching mechanism 12.

(1-2) Cooling-to-Heating Transition Operation

The refrigeration cycle apparatus 1 performs a cooling-to-heating transition operation for making a transition from a cycle state for performing the cooling operation to a cycle state for performing the heating operation.

In the cooling-to-heating transition operation, first, the third expansion valve 14 is controlled to be in a fully closed state from the state in which the cooling operation is performed, the connection state of the first switching mechanism 12 is switched to a state in which the discharge side of the first compressor 11 is connected to the gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 and the suction side of the first compressor 11 is connected to the first on-off valve 41 and the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17, and the first compressor 11 is operated, with the second on-off valve 42 closed and the first expansion valve 15 and the second expansion valve 16 controlled to be in the fully closed state. After this operation state is maintained for a while, the first on-off valve 41 is closed. As a result, the first refrigerant can be collected in a flow path from the first on-off valve 41 to the third expansion valve 14 via the first compressor 11 and the use heat exchanger 13.

Then, opening the first expansion valve 15 while maintaining the third expansion valve 14 in the fully closed state and also maintaining the first on-off valve 41 in the closed state allows the first refrigerant to circulate through the first compressor 11, the use heat exchanger 13, the first expansion valve 15, and the cascade heat exchanger 17. Further, opening the second expansion valve 16 and the second on-off valve 42 allows the second refrigerant to circulate through the second compressor 21, the cascade heat exchanger 17, the second expansion valve 16, and the outdoor heat exchanger 18.

Thus, the cooling-to-heating transition operation is completed.

(1-3) Heating Operation

During the heating operation, as illustrated in FIG. 4 , a two-stage refrigeration cycle is performed in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. In FIG. 4 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as a condenser of the first refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, and the outdoor heat exchanger 18 is caused to function as an evaporator of the second refrigerant.

Specifically, in this two-stage refrigeration cycle, the third expansion valve 14 is controlled to be in a fully closed state, and the first on-off valve 41 is controlled to be in a closed state to prevent mixing of the first refrigerant and the second refrigerant. The connection state of the first switching mechanism 12 is switched to a connection state indicated by broken lines in FIG. 4 , the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven, and the second on-off valve 42 is controlled to be in an open state. Further, the valve opening degree of the first expansion valve 15 is controlled such that the degree of superheating of the first refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the second expansion valve 16 is controlled such that the degree of superheating of the second refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the second refrigerant discharged from the second compressor 21 is sent to the cascade heat exchanger 17. When flowing through the second cascade flow path 17 b, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the first cascade flow path 17 a. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, is decompressed in the second expansion valve 16. After that, the second refrigerant is evaporated by heat exchange with the outdoor air supplied by the outdoor fan 9 in the outdoor heat exchanger 18, and is sucked into the second compressor 21. The first refrigerant discharged from the first compressor 11 is sent to the first use flow path 13 a of the use heat exchanger 13 via the first switching mechanism 12. The first refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is condensed by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water heated by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the heating load. The first refrigerant condensed in the first use flow path 13 a of the use heat exchanger 13 passes through the branch point A and is then decompressed in the first expansion valve 15. The first refrigerant decompressed by the first expansion valve 15 is evaporated, when passing through the first cascade flow path 17 a of the cascade heat exchanger 17, by heat exchange with the second refrigerant flowing through the second cascade flow path 17 b. The first refrigerant evaporated in the first cascade flow path 17 a of the cascade heat exchanger 17 is sucked into the first compressor 11 via the first switching mechanism 12.

(1-4) Heating-to-Cooling Transition Operation

The refrigeration cycle apparatus 1 performs a heating-to-cooling transition operation for making a transition from a cycle state for performing the heating operation to a cycle state for performing the cooling operation.

In the heating-to-cooling transition operation, first, the second expansion valve 16 is controlled to be in a fully closed state from the state in which the heating operation is performed, and the second compressor 21 is driven, with the third expansion valve 14 also maintained in the fully closed state. After this operation state is maintained for a while, the second on-off valve 42 is closed. As a result, the second refrigerant can be collected in a flow path from the second on-off valve 42 to the second expansion valve 16 via the second compressor 21 and the second cascade flow path 17 b of the cascade heat exchanger 17.

Then, the first expansion valve 15 is controlled to be in a fully closed state, the third expansion valve 14 and the first on-off valve 41 is opened, and the first switching mechanism 12 is brought into a state in which the discharge side of the first compressor 11 is connected to the first on-off valve 41 and the suction side of the first compressor 11 is connected to the gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 and the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17. This makes it possible to perform a cooling operation based on a single-stage refrigeration cycle using the first refrigerant.

Thus, the heating-to-cooling transition operation is completed.

(1-5) Features of First Embodiment

In the refrigeration cycle apparatus 1 according to the first embodiment, the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP) and the second refrigerant having a sufficiently low ozone depletion potential (ODP) and a sufficiently low global warming potential (GWP). Thus, global environmental deterioration can be reduced.

In addition, even when the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP), the two-stage refrigeration cycle in which the second refrigerant, which is a high-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the first refrigerant, which is a low-pressure refrigerant, is used in the use-side refrigeration cycle is performed as the heating operation. This makes it easier to secure heating operation capacity than a single-stage refrigeration cycle using the first refrigerant, which is a low-pressure refrigerant.

Further, the refrigerant circuit 10 uses carbon dioxide as the second refrigerant. However, during the cooling operation, a single-stage refrigeration cycle using the second refrigerant is not performed, nor is performed a two-stage refrigeration cycle in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. Instead of this, a single-stage refrigeration cycle using the first refrigerant is performed. This makes it possible to perform the cooling operation without causing a reduction in COP, as in the case of performing a single-stage refrigeration cycle using a carbon dioxide refrigerant, which is a high-pressure refrigerant, or as in the case of performing a two-stage refrigeration cycle in which carbon dioxide, which is a high-pressure refrigerant, is used in the heat-source-side cycle, the reduction in COP being due to the pressure of the carbon dioxide refrigerant exceeding the critical pressure. It is also possible to reduce the compression strength standards required for the components of the refrigerant circuit 10 in which carbon dioxide, which is a high-pressure refrigerant, is used.

(2) Second Embodiment

FIG. 5 is a schematic configuration diagram of a refrigeration cycle apparatus 1 a according to a second embodiment. FIG. 6 is a functional block configuration diagram of the refrigeration cycle apparatus 1 a according to the second embodiment.

The refrigeration cycle apparatus 1 a is an apparatus used to process a heat load through a vapor-compression refrigeration cycle operation. The refrigeration cycle apparatus 1 a includes a heat-load circuit 90, a refrigerant circuit 10, an outdoor fan 9, and a controller 7.

The heat load to be processed by the refrigeration cycle apparatus 1 a and the heat-load circuit 90 are similar to those according to the first embodiment.

In the present embodiment, as described below, a use heat exchanger 13 includes a first use flow path 13 a through which a first refrigerant or a second refrigerant flowing through the refrigerant circuit 10 passes. Water flowing through a heat-load flow path 13 b of the use heat exchanger 13 exchanges heat with the first refrigerant or second refrigerant flowing through the first use flow path 13 a. As a result, the water is cooled during a cooling operation and is heated during a heating operation.

The refrigerant circuit 10 includes a first compressor 11, a second compressor 21, a first switching mechanism 12, a second switching mechanism 22, the use heat exchanger 13 shared with the heat-load circuit 90, a first expansion valve 15, a second expansion valve 16, a cascade heat exchanger 17, an outdoor heat exchanger 18, a refrigerant container 19, a third on-off valve 43, a fourth on-off valve 44, a fifth on-off valve 45, a sixth on-off valve 46, a seventh on-off valve 47, an eighth on-off valve 48, and a ninth on-off valve 49.

The refrigerant circuit 10 is filled with the first refrigerant, which is a low-pressure refrigerant, and the second refrigerant, which is a high-pressure refrigerant, as refrigerants in a substantially separated state. The first refrigerant is a refrigerant having 1 MPa or less at 30° C., and is a refrigerant including, for example, at least one of R1234yf or R1234ze. The first refrigerant may include only R1234yf or may include only R1234ze. The second refrigerant is a refrigerant having 1.5 MPa or more at 30° C. For example, the second refrigerant may include carbon dioxide, or may include only carbon dioxide.

The specific configuration of the first compressor 11 is similar to that according to the first embodiment. A discharge side of the first compressor 11 is connected to a first port of a switching valve 12 a of the first switching mechanism 12. A suction side of the first compressor 11 is connected to a branch point D1.

The branch point D1 is connected to a second port of the switching valve 12 a of the first switching mechanism 12, a second port of a switching valve 12 b of the first switching mechanism 12, and a flow path extending from the eighth on-off valve 48.

The first switching mechanism 12 includes the switching valve 12 a and the switching valve 12 b.

In the present embodiment, the switching valve 12 a is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port of the switching valve 12 a is connected to the discharge side of the first compressor 11. The second port of the switching valve 12 a is connected to the suction side of the first compressor 11. The third port of the switching valve 12 a is connected to a flow path extending from a branch point E2. The fourth port of the switching valve 12 a is connected to a first port of the switching valve 12 b.

In the present embodiment, the switching valve 12 b is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port of the switching valve 12 b is connected to the fourth port of the switching valve 12 a. The second port of the switching valve 12 b is connected to the suction side of the first compressor 11. The third port of the switching valve 12 b is connected to a gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13. The fourth port of the switching valve 12 b is connected to a gas refrigerant side of a first cascade flow path 17 a of the cascade heat exchanger 17.

The switching valve 12 a switches between a state in which the discharge side of the first compressor 11 is connected to the first port of the switching valve 12 b and the suction side of the first compressor 11 is connected to the branch point E2 and a state in which the discharge side of the first compressor 11 is connected to the branch point E2 and the suction side of the first compressor 11 is connected to the first port of the switching valve 12 b.

The switching valve 12 b switches between a state in which the fourth port of the switching valve 12 a is connected to the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17 and the suction side of the first compressor 11 is connected to the gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 and a state in which the fourth port of the switching valve 12 a is connected to the gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 and the suction side of the first compressor 11 is connected to the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17.

The gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 through which the refrigerant flowing through the refrigerant circuit 10 passes is connected to the switching valve 12 b of the first switching mechanism 12. A liquid refrigerant side of the first use flow path 13 a is connected to a branch point A included in the refrigerant circuit 10.

At the branch point A, a flow path extending from the liquid refrigerant side of the first use flow path 13 a, a flow path extending to the side of the first expansion valve 15 opposite to the cascade heat exchanger 17 side, and a flow path extending from a branch point J are connected.

The first expansion valve 15 is configured as an electronic expansion valve that is adjustable in valve opening degree. In the refrigerant circuit 10, the first expansion valve 15 is disposed at a certain point in a flow path connecting the branch point A and a branch point F.

The branch point F connects a flow path extending from the first expansion valve 15, a flow path extending from a branch point H1, and a flow path extending from a liquid refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17.

The cascade heat exchanger 17 is a cascade heat exchanger that includes the first cascade flow path 17 a through which one of the first refrigerant and the second refrigerant passes and a second cascade flow path 17 b through which the other of the first refrigerant and the second refrigerant passes, and that exchanges heat between the first refrigerant and the second refrigerant. In the cascade heat exchanger 17, the first cascade flow path 17 a and the second cascade flow path 17 b are independent of each other, and the first refrigerant and the second refrigerant do not mix with each other in the cascade heat exchanger 17. The gas refrigerant side of the first cascade flow path 17 a is connected to the switching valve 12 b of the first switching mechanism 12. The liquid refrigerant side of the first cascade flow path 17 a is connected to a flow path extending from the branch point F. A gas refrigerant side of the second cascade flow path 17 b is connected to a switching valve 22 b of the second switching mechanism 22. A liquid refrigerant side of the second cascade flow path 17 b is connected to a flow path extending from a branch point G.

The specific configuration of the second compressor 21 is similar to that according to the first embodiment. A discharge side of the second compressor 21 is connected to a first port of a switching valve 22 a of the second switching mechanism 22. A suction side of the second compressor 21 is connected to a branch point E1.

The branch point E1 is connected to a second port of the switching valve 22 a of the second switching mechanism 22, a second port of the switching valve 22 b of the second switching mechanism 22, and a flow path extending from the seventh on-off valve 47.

The second switching mechanism 22 includes the switching valve 22 a and the switching valve 22 b.

In the present embodiment, the switching valve 22 a is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port of the switching valve 22 a is connected to the discharge side of the second compressor 21. The second port of the switching valve 22 a is connected to the suction side of the second compressor 21. The third port of the switching valve 22 a is connected to a flow path extending from a branch point D2. The fourth port of the switching valve 22 a is connected to a first port of the switching valve 22 b.

In the present embodiment, the switching valve 22 b is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port of the switching valve 22 b is connected to the fourth port of the switching valve 22 a. The second port of the switching valve 22 b is connected to the suction side of the second compressor 21. The third port of the switching valve 22 b is connected to the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17. The fourth port of the switching valve 22 b is connected to a gas refrigerant side of the outdoor heat exchanger 18.

The switching valve 22 a switches between a state in which the discharge side of the second compressor 21 is connected to the first port of the switching valve 22 b and the suction side of the second compressor 21 is connected to the branch point D2 and a state in which the discharge side of the second compressor 21 is connected to the branch point D2 and the suction side of the second compressor 21 is connected to the first port of the switching valve 22 b.

The switching valve 22 b switches between a state in which the fourth port of the switching valve 22 a is connected to the gas refrigerant side of the outdoor heat exchanger 18 and the suction side of the second compressor 21 is connected to the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 and a state in which the fourth port of the switching valve 22 a is connected to the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 and the suction side of the second compressor 21 is connected to the gas refrigerant side of the outdoor heat exchanger 18.

The branch point G is connected to a flow path extending from the liquid refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17, a flow path extending from the second expansion valve 16, and a flow path extending from a branch point H2.

The second expansion valve 16 is configured as an electronic expansion valve that is adjustable in valve opening degree. The second expansion valve 16 is disposed between the branch point G and the liquid refrigerant side of the outdoor heat exchanger 18.

The outdoor heat exchanger 18 includes a plurality of heat transfer tubes and a plurality of fins joined to the plurality of heat transfer tubes. In the present embodiment, the outdoor heat exchanger 18 is arranged outdoors. A refrigerant flowing through the outdoor heat exchanger 18 exchanges heat with air sent to the outdoor heat exchanger 18.

The outdoor fan 9 generates an air flow of outdoor air passing through the outdoor heat exchanger 18.

The branch point J is connected to a flow path extending from the branch point A, a flow path extending from the sixth on-off valve 46, and a flow path extending from a branch point K1. The branch point K1 connects a flow path extending from the branch point J, a flow path extending from an upper end portion of the refrigerant container 19, and a flow path extending from the ninth on-off valve 49. The ninth on-off valve 49 is disposed at a certain point in a flow path connecting the branch point D2 and the branch point K1. The branch point D2 connects a flow path extending from the ninth on-off valve 49, a flow path extending from the eighth on-off valve 48, and a flow path extending from the third port of the switching valve 22 a of the second switching mechanism 22. The eighth on-off valve 48 is disposed at a certain point in a flow path connecting the branch point D2 and the branch point D1. The sixth on-off valve 46 is disposed at a certain point in a flow path connecting the branch point J and the branch point E2. The branch point E2 connects a flow path extending from the seventh on-off valve 47, a flow path extending from the sixth on-off valve 46, and a flow path extending from the third port of the switching valve 12 a of the first switching mechanism 12. The seventh on-off valve 47 is disposed at a certain point in a flow path connecting the branch point E1 and the branch point E2.

A branch point K2 connects a flow path extending from a lower end portion of the refrigerant container 19, a flow path extending from the fourth on-off valve 44, and a flow path extending from the fifth on-off valve 45. The fourth on-off valve 44 is disposed at a certain point in a flow path connecting the branch point K2 and the branch point H1. The fifth on-off valve 45 is disposed at a certain point in a flow path connecting the branch point K2 and the branch point H2. The branch point H1 connects a flow path extending from the third on-off valve 43, a flow path extending from the fourth on-off valve 44, and a flow path extending from the branch point F. The branch point H2 connects a flow path extending from the third on-off valve 43, a flow path extending from the fifth on-off valve 45, and a flow path extending from the branch point G. The third on-off valve 43 is disposed at a certain point in a flow path connecting the branch point H1 and the branch point H2.

The third on-off valve 43, the fourth on-off valve 44, the fifth on-off valve 45, the sixth on-off valve 46, the seventh on-off valve 47, the eighth on-off valve 48, and the ninth on-off valve 49 are each an electromagnetic valve controllable to switch between an open state and a closed state.

The refrigerant container 19 is a container capable of holding therein the first refrigerant or the second refrigerant. The refrigerant container 19 can be used to move the second refrigerant within the refrigerant circuit 10 while the first refrigerant is stored in the refrigerant container 19 or to move the first refrigerant within the refrigerant circuit 10 while the second refrigerant is stored in the refrigerant container 19. The refrigerant container 19 has a capacity such that the refrigerant container 19 can store the first refrigerant and store the second refrigerant. In the present embodiment, the refrigerant container 19 used to move the first refrigerant within the refrigerant circuit 10 while the second refrigerant is stored in the refrigerant container 19 will be described as an example.

The controller 7 controls the operation of the devices included in the heat-load circuit 90 and the refrigerant circuit 10. Specifically, the controller 7 includes a processor serving as a CPU provided for performing control, a memory, and the like.

In the refrigeration cycle apparatus 1 a described above, the controller 7 controls the devices to execute a refrigeration cycle, thereby performing a cooling operation for processing a cooling load in the heat-load heat exchanger 91, a heating operation for processing a heating load in the heat-load heat exchanger 91, a cooling-to-heating transition operation, and a heating-to-cooling transition operation.

(2-1) Cooling Operation

During the cooling operation, as illustrated in FIG. 7 , a two-stage refrigeration cycle operation is performed in which the first refrigerant is used in a heat-source-side refrigeration cycle and the second refrigerant is used in a use-side refrigeration cycle. In FIG. 7 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as an evaporator of the second refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, and the outdoor heat exchanger 18 is caused to function as a condenser of the first refrigerant.

Specifically, in this two-stage refrigeration cycle, all of the third on-off valve 43, the fourth on-off valve 44, the fifth on-off valve 45, the sixth on-off valve 46, the seventh on-off valve 47, the eighth on-off valve 48, and the ninth on-off valve 49 are controlled to be in a closed state to prevent mixing of the first refrigerant and the second refrigerant. Then, a connection state of the first switching mechanism 12 is switched to a connection state indicated by solid lines in FIG. 7 , a connection state of the second switching mechanism 22 is switched to a connection state indicated by solid lines in FIG. 7 , and the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven. Further, the valve opening degree of the first expansion valve 15 is controlled such that the degree of superheating of the second refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the second expansion valve 16 is controlled such that the degree of superheating of the first refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the first refrigerant discharged from the second compressor 21 is sent to the outdoor heat exchanger 18 via the switching valve 22 a and the switching valve 22 b of the second switching mechanism 22. The first refrigerant flowing through the outdoor heat exchanger 18 is condensed by heat exchange with the outdoor air supplied by the outdoor fan 9. The first refrigerant condensed in the outdoor heat exchanger 18 is decompressed in the second expansion valve 16, passes through the branch point G, and is sent to the second cascade flow path 17 b of the cascade heat exchanger 17. When flowing through the second cascade flow path 17 b of the cascade heat exchanger 17, the first refrigerant is evaporated by heat exchange with the second refrigerant flowing through the first cascade flow path 17 a. The first refrigerant evaporated in the cascade heat exchanger 17 is sucked into the second compressor 21 via the switching valve 22 b of the second switching mechanism 22. The second refrigerant discharged from the first compressor 11 is sent to the first cascade flow path 17 a of the cascade heat exchanger 17 via the switching valve 12 a and the switching valve 12 b of the first switching mechanism 12. When flowing through the first cascade flow path 17 a of the cascade heat exchanger 17, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the second cascade flow path 17 b. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, passes through the branch point F, is decompressed in the first expansion valve 15, passes through the branch point A. and is sent to the first use flow path 13 a of the use heat exchanger 13. The second refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is evaporated by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water cooled by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the cooling load. The second refrigerant evaporated in the first use flow path 13 a of the use heat exchanger 13 is sucked into the first compressor 11 via the switching valve 12 b of the first switching mechanism 12.

(2-2) Cooling-to-Heating Transition Operation

The refrigeration cycle apparatus 1 a performs a cooling-to-heating transition operation including (a1) to (f1) below in this order to make a transition from a cycle state for performing the cooling operation to a cycle state for performing the heating operation.

-   -   (a1) First, the first expansion valve 15 is controlled to be in         a fully closed state from the state in which the cooling         operation is performed, and the first compressor 1 l is         operated, with the fourth on-off valve 44 opened. Here, the         second compressor 21 and the like are operated such that the         refrigeration cycle for the cooling operation using the first         refrigerant is performed. As a result, an operation of         recovering the second refrigerant into the refrigerant container         19 from below the refrigerant container 19 is performed. At this         time, the sixth on-off valve 46 is controlled to switch between         the open state and the closed state at predetermined time         intervals, thereby allowing the gaseous second refrigerant in a         flow path from an upper end of the refrigerant container 19 to         the sixth on-off valve 46 to be sucked into the first compressor         11. This provides efficient recovery of the second refrigerant         into the refrigerant container 19. This operation is continued         for a predetermined period of time, for example, until a         predetermined sufficient amount of the second refrigerant is         recovered in the refrigerant container 19.     -   (b1) Then, the fourth on-off valve 44 is closed after the second         refrigerant has been recovered into the refrigerant container 19         by a predetermined amount or more. After that, the switching         valve 12 a is switched to a state in which the discharge side of         the first compressor 11 is connected to the branch point E2 and         the suction side of the first compressor 11 is connected to the         first port of the switching valve 12 b, and the switching valve         12 b is switched to a state in which the fourth port of the         switching valve 12 a is connected to the gas refrigerant side of         the first use flow path 13 a of the use heat exchanger 13 and         the suction side of the first compressor 11 is connected to the         gas refrigerant side of the first cascade flow path 17 a of the         cascade heat exchanger 17. Further, the switching valve 22 a is         switched to a state in which the discharge side of the second         compressor 21 is connected to the first port of the switching         valve 22 b and the suction side of the second compressor 21 is         connected to the branch point D2, and the switching valve 22 b         is switched to a state in which the fourth port of the switching         valve 22 a is connected to the gas refrigerant side of the         second cascade flow path 17 b of the cascade heat exchanger 17         and the suction side of the second compressor 21 is connected to         the gas refrigerant side of the outdoor heat exchanger 18. In         this state, the sixth on-off valve 46 is controlled to be in an         open state, and the first compressor 11 and the second         compressor 21 are operated to heat and expel the second         refrigerant remaining in the first cascade flow path 17 a of the         cascade heat exchanger 17 by using the heat of the first         refrigerant. Then, the second refrigerant is collected in the         refrigerant container 19 via the first compressor 11, the branch         point E2, the sixth on-off valve 46, the branch point J. and the         branch point K1. After this operation is continued for a         predetermined period of time, the sixth on-off valve 46 is         controlled to be in a closed state, and the recovery of the         second refrigerant into the refrigerant container 19 is         completed.     -   (c1) Then, the switching valve 12 a is switched to a state in         which the discharge side of the first compressor 11 is connected         to the first port of the switching valve 12 b and the suction         side of the first compressor 11 is connected to the branch point         E2, and the switching valve 12 b is switched to a state in which         the fourth port of the switching valve 12 a is connected to the         gas refrigerant side of the first use flow path 13 a of the use         heat exchanger 13 and the suction side of the first compressor         11 is connected to the gas refrigerant side of the first cascade         flow path 17 a of the cascade heat exchanger 17. In this state,         the second expansion valve 16 is controlled to be in a fully         closed state, the third on-off valve 43 is opened while the         fourth on-off valve 44 and the fifth on-off valve 45 are         maintained in the closed state, and the first compressor 11 and         the second compressor 21 are operated. As a result, the first         refrigerant existing in a portion from the second expansion         valve 16 to the suction side of the second compressor 21 is sent         to the first cascade flow path 17 a of the cascade heat         exchanger 17 via the second switching mechanism 22, the second         cascade flow path 17 b of the cascade heat exchanger 17, the         branch point G, the branch point H2, the third on-off valve 43,         the branch point H1, and the branch point F. Further, the first         refrigerant is sucked into the first compressor 11 via the         switching valve 12 b of the first switching mechanism 12. Then,         the first refrigerant discharged from the first compressor 11 is         sent to the use heat exchanger 13 via the switching valve 12 a         of the first switching mechanism 12.     -   (d1) Then, the third on-off valve 43 is closed, and the eighth         on-off valve 48 is opened. The switching valve 22 a is switched         to a state in which the discharge side of the second compressor         21 is connected to the branch point D2 and the suction side of         the second compressor 21 is connected to the first port of the         switching valve 22 b, and the switching valve 22 b is switched         to a state in which the fourth port of the switching valve 22 a         is connected to the gas refrigerant side of the outdoor heat         exchanger 18 and the suction side of the second compressor 21 is         connected to the gas refrigerant side of the second cascade flow         path 17 b of the cascade heat exchanger 17. In this state, the         first compressor 11 and the second compressor 21 are operated to         discharge, from the second compressor 21, the first refrigerant         existing in a portion from the third on-off valve 43 to the         suction side of the second compressor 21. Then, the first         refrigerant is sucked into the first compressor 11 via the         branch point D2, the eighth on-off valve 48, and the branch         point D1.     -   (e1) Then, the eighth on-off valve 48 is closed, the first         expansion valve 15 is opened, with the opening degree thereof         controlled. The switching valve 12 a is switched to a state in         which the discharge side of the first compressor 11 is connected         to the first port of the switching valve 12 b and the suction         side of the first compressor 11 is connected to the branch point         E2, and the switching valve 12 b is switched to a state in which         the fourth port of the switching valve 12 a is connected to the         gas refrigerant side of the first cascade flow path 17 a of the         cascade heat exchanger 17 and the suction side of the first         compressor 11 is connected to the gas refrigerant side of the         first use flow path 13 a of the use heat exchanger 13. Further,         the fifth on-off valve 45 is opened, with the second expansion         valve 16 maintained in the fully closed state. The switching         valve 22 a is switched to a state in which the discharge side of         the second compressor 21 is connected to the first port of the         switching valve 22 b and the suction side of the second         compressor 21 is connected to the branch point D2, and the         switching valve 22 b is switched to a state in which the fourth         port of the switching valve 22 a is connected to the gas         refrigerant side of the outdoor heat exchanger 18 and the         suction side of the second compressor 21 is connected to the gas         refrigerant side of the second cascade flow path 17 b of the         cascade heat exchanger 17. In this state, the first compressor         11 and the second compressor 21 are operated. As a result, the         second refrigerant stored in the refrigerant container 19 is         drawn into the second cascade flow path 17 b of the cascade heat         exchanger 17 via the branch point K2, the fifth on-off valve 45,         the branch point H2, and the branch point G. At this time, the         second refrigerant flowing through the second cascade flow path         17 b of the cascade heat exchanger 17 is heated by heat exchange         with the first refrigerant flowing through the first cascade         flow path 17 a of the cascade heat exchanger 17. After that, the         heated second refrigerant is sent to the second compressor 21         via the switching valve 22 b. The second refrigerant is further         discharged from the second compressor 21, passes through the         switching valve 22 a and the switching valve 22 b, and is then         stored in the outdoor heat exchanger 18.     -   (f1) Finally, the fifth on-off valve 45 is closed and the ninth         on-off valve 49 is opened, with the second expansion valve 16         maintained in the fully closed state while the connection state         of the second switching mechanism 22 is maintained. The         switching valve 12 b is switched to a state in which the fourth         port of the switching valve 12 a is connected to the gas         refrigerant side of the first use flow path 13 a of the use heat         exchanger 13 and the suction side of the first compressor 11 is         connected to the gas refrigerant side of the first cascade flow         path 17 a of the cascade heat exchanger 17. In this state, the         second compressor 21 is operated, and the first compressor 11 is         operated or stopped. As a result, the gaseous second refrigerant         remaining in an upper portion of the refrigerant container 19         can be sucked into the second compressor 21 via the branch point         K1, the ninth on-off valve 49, the branch point D2, and the         switching valve 22 a. After the refrigerant container 19 is         emptied through this operation, the ninth on-off valve 49 is         closed.

Thus, the cooling-to-heating transition operation is completed.

(2-3) Heating Operation

During the heating operation, as illustrated in FIG. 8 , a two-stage refrigeration cycle is performed in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. In FIG. 8 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as a condenser of the first refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, and the outdoor heat exchanger 18 is caused to function as an evaporator of the second refrigerant.

Specifically, in this two-stage refrigeration cycle, all of the third on-off valve 43, the fourth on-off valve 44, the fifth on-off valve 45, the sixth on-off valve 46, the seventh on-off valve 47, the eighth on-off valve 48, and the ninth on-off valve 49 are controlled to be in a closed state to prevent mixing of the first refrigerant and the second refrigerant. Then, a connection state of the switching valve 12 a of the first switching mechanism 12 is changed to a state indicated by solid lines in FIG. 8 , a connection state of the switching valve 12 b of the first switching mechanism 12 is changed to a state indicated by broken lines in FIG. 8 , a connection state of the switching valve 22 a of the second switching mechanism 22 is changed to a state indicated by solid lines in FIG. 8 , a connection state of the switching valve 22 b of the second switching mechanism 22 is switched to a connection state indicated by broken lines in FIG. 8 , and the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven. Further, the valve opening degree of the first expansion valve 15 is controlled such that the degree of superheating of the first refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the second expansion valve 16 is controlled such that the degree of superheating of the second refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the second refrigerant discharged from the second compressor 21 is sent to the cascade heat exchanger 17. When flowing through the second cascade flow path 17 b, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the first cascade flow path 17 a. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, is decompressed in the second expansion valve 16. After that, the second refrigerant is evaporated by heat exchange with the outdoor air supplied by the outdoor fan 9 in the outdoor heat exchanger 18, and is sucked into the second compressor 21. The first refrigerant discharged from the first compressor 11 is sent to the first use flow path 13 a of the use heat exchanger 13 via the first switching mechanism 12. The first refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is condensed by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water heated by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the heating load. The first refrigerant condensed in the first use flow path 13 a of the use heat exchanger 13 passes through the branch point A and is then decompressed in the first expansion valve 15. The first refrigerant decompressed by the first expansion valve 15 is evaporated, when passing through the first cascade flow path 17 a of the cascade heat exchanger 17, by heat exchange with the second refrigerant flowing through the second cascade flow path 17 b. The first refrigerant evaporated in the first cascade flow path 17 a of the cascade heat exchanger 17 is sucked into the first compressor 11 via the first switching mechanism 12.

(2-4) Heating-to-Cooling Transition Operation

The refrigeration cycle apparatus 1 a performs a heating-to-cooling transition operation including (a2) to (f2) below in this order to make a transition from a cycle state for performing the heating operation to a cycle state for performing the cooling operation.

-   -   (a2) First, the second expansion valve 16 is controlled to be in         a fully closed state from the state in which the heating         operation is performed, the fifth on-off valve 45 is controlled         to be in an open state, and the second compressor 21 is         operated. Here, the first compressor 11 and the like are         operated such that the use-side refrigeration cycle for the         heating operation using the first refrigerant is maintained. As         a result, an operation of recovering the second refrigerant into         the refrigerant container 19 from below the refrigerant         container 19 is performed. At this time, the ninth on-off valve         49 is controlled to switch between the open state and the closed         state at predetermined time intervals, thereby allowing the         gaseous second refrigerant in a flow path from the upper end of         the refrigerant container 19 to the ninth on-off valve 49 to be         sucked into the second compressor 21. This provides efficient         recovery of the second refrigerant into the refrigerant         container 19. This operation is continued for a predetermined         period of time, for example, until a predetermined sufficient         amount of the second refrigerant is recovered in the refrigerant         container 19.     -   (b2) Then, the fifth on-off valve 45 is closed after the second         refrigerant has been recovered into the refrigerant container 19         by a predetermined amount or more. After that, the switching         valve 12 a is switched to a state in which the discharge side of         the first compressor 11 is connected to the first port of the         switching valve 12 b and the suction side of the first         compressor 11 is connected to the branch point E2, and the         switching valve 12 b is switched to a state in which the fourth         port of the switching valve 12 a is connected to the gas         refrigerant side of the first cascade flow path 17 a of the         cascade heat exchanger 17 and the suction side of the first         compressor 11 is connected to the gas refrigerant side of the         first use flow path 13 a of the use heat exchanger 13. Further,         the switching valve 22 a is switched to a state in which the         discharge side of the second compressor 21 is connected to the         branch point D2 and the suction side of the second compressor 21         is connected to the first port of the switching valve 22 b, and         the switching valve 22 b is switched to a state in which the         fourth port of the switching valve 22 a is connected to the gas         refrigerant side of the outdoor heat exchanger 18 and the         suction side of the second compressor 21 is connected to the gas         refrigerant side of the second cascade flow path 17 b of the         cascade heat exchanger 17. In this state, the ninth on-off valve         49 is opened, and the first compressor 11 and the second         compressor 21 are operated to heat and expel the second         refrigerant remaining in the second cascade flow path 17 b of         the cascade heat exchanger 17 by using the heat of the first         refrigerant. Then, the second refrigerant is collected in the         refrigerant container 19 via the second compressor 21, the         branch point D2, the ninth on-off valve 49, and the branch point         K1. After this operation is continued for a predetermined period         of time, the ninth on-off valve 49 is controlled to be in a         closed state, and the recovery of the second refrigerant into         the refrigerant container 19 is completed.     -   (c2) Then, the switching valve 22 a is switched to a state in         which the discharge side of the second compressor 21 is         connected to the first port of the switching valve 22 b and the         suction side of the second compressor 21 is connected to the         branch point D2, and the switching valve 22 b is changed to a         state in which the fourth port of the switching valve 22 a is         connected to the gas refrigerant side of the outdoor heat         exchanger 18 and the suction side of the second compressor 21 is         connected to the gas refrigerant side of the second cascade flow         path 17 b of the cascade heat exchanger 17. In this state, the         first expansion valve 15 is controlled to be in a fully closed         state, the third on-off valve 43 is opened while the fourth         on-off valve 44 and the fifth on-off valve 45 are maintained in         the closed state, and the first compressor 11 and the second         compressor 21 are operated. As a result, the first refrigerant         existing in a portion from the first expansion valve 15 to the         suction side of the first compressor 11 is sent to the second         cascade flow path 17 b of the cascade heat exchanger 17 via the         first switching mechanism 12, the first cascade flow path 17 a         of the cascade heat exchanger 17, the branch point F, the branch         point H1, the third on-off valve 43, the branch point H2, and         the branch point G. Further, the first refrigerant is sucked         into the second compressor 21 via the switching valve 22 b of         the second switching mechanism 22. The first refrigerant         discharged from the second compressor 21 is sent to the outdoor         heat exchanger 18 via the switching valve 22 a of the second         switching mechanism 22.     -   (d2) Then, the third on-off valve 43 is closed, the seventh         on-off valve 47 is opened, the switching valve 12 a is switched         to a state in which the discharge side of the first compressor         11 is connected to the branch point E2 and the suction side of         the first compressor 11 is connected to the first port of the         switching valve 12 b, and the switching valve 12 b is switched         to a state in which the fourth port of the switching valve 12 a         is connected to the gas refrigerant side of the first use flow         path 13 a of the use heat exchanger 13 and the suction side of         the first compressor 11 is connected to the gas refrigerant side         of the first cascade flow path 17 a of the cascade heat         exchanger 17. In this state, the first compressor 11 and the         second compressor 21 are operated to discharge, from the first         compressor 11, the first refrigerant existing in a portion from         the third on-off valve 43 to the suction side of the first         compressor 11. Then, the first refrigerant is sucked into the         second compressor 21 through the branch point E2, the seventh         on-off valve 47, and the branch point E1.     -   (e2) Then, the seventh on-off valve 47 is closed, the second         expansion valve 16 is opened, with the opening degree thereof         controlled. The switching valve 22 a is switched to a state in         which the discharge side of the second compressor 21 is         connected to the first port of the switching valve 22 b and the         suction side of the second compressor 21 is connected to the         branch point D2, and the switching valve 22 b is switched to a         state in which the fourth port of the switching valve 22 a is         connected to the gas refrigerant side of the second cascade flow         path 17 b of the cascade heat exchanger 17 and the suction side         of the second compressor 21 is connected to the gas refrigerant         side of the outdoor heat exchanger 18. Further, the fourth         on-off valve 44 is opened, with the first expansion valve 15         maintained in the fully closed state. The switching valve 12 a         is switched to a state in which the discharge side of the first         compressor 11 is connected to the first port of the switching         valve 12 b and the suction side of the first compressor 11 is         connected to the branch point E2, and the switching valve 12 b         is switched to a state in which the fourth port of the switching         valve 12 a is connected to the gas refrigerant side of the first         use flow path 13 a of the use heat exchanger 13 and the suction         side of the first compressor 11 is connected to the gas         refrigerant side of the first cascade flow path 17 a of the         cascade heat exchanger 17. In this state, the first compressor         11 and the second compressor 21 are operated. As a result, the         second refrigerant stored in the refrigerant container 19 is         drawn into the first cascade flow path 17 a of the cascade heat         exchanger 17 via the branch point K2, the fourth on-off valve         44, the branch point H1, and the branch point F. At this time,         the second refrigerant flowing through the first cascade flow         path 17 a of the cascade heat exchanger 17 is heated by heat         exchange with the first refrigerant flowing through the second         cascade flow path 17 b of the cascade heat exchanger 17. After         that, the heated second refrigerant is sent to the first         compressor 11 via the switching valve 12 b. The second         refrigerant is further discharged from the first compressor 11,         passes through the switching valve 12 a and the switching valve         12 b, and is then stored in the use heat exchanger 13.     -   (f2) Finally, the fourth on-off valve 44 is closed and the sixth         on-off valve 46 is opened, with the first expansion valve 15         maintained in the fully closed state while the connection state         of the first switching mechanism 12 is maintained. In this         state, the first compressor 11 is operated, and the second         compressor 21 is operated or stopped. As a result, the gaseous         second refrigerant remaining in the upper portion of the         refrigerant container 19 can be sucked into the first compressor         11 via the branch point K1, the branch point J, the sixth on-off         valve 46, the branch point E2, and the switching valve 12 a.         After the refrigerant container 19 is emptied through this         operation, the sixth on-off valve 46 is closed.

Thus, the heating-to-cooling transition operation is completed.

(2-5) Features of Second Embodiment

In the refrigeration cycle apparatus 1 a according to the second embodiment, the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP) and the second refrigerant having a sufficiently low ozone depletion potential (ODP) and a sufficiently low global warming potential (GWP). Thus, global environmental deterioration can be reduced.

In addition, even when the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP), the two-stage refrigeration cycle in which the second refrigerant, which is a high-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the first refrigerant, which is a low-pressure refrigerant, is used in the use-side refrigeration cycle is performed as the heating operation. This makes it easier to secure heating operation capacity than a single-stage refrigeration cycle using the first refrigerant, which is a low-pressure refrigerant.

Further, the refrigerant circuit 10 uses carbon dioxide as the second refrigerant. However, during the cooling operation, a single-stage refrigeration cycle using the second refrigerant is not performed, nor is performed a two-stage refrigeration cycle in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. Instead of this, a two-stage refrigeration cycle in which the first refrigerant, which is a low-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the second refrigerant, which is a high-pressure refrigerant, is used in the use-side refrigeration cycle is performed. This makes it possible to perform the cooling operation without causing a reduction in COP, as in the case of performing a single-stage refrigeration cycle using a carbon dioxide refrigerant, which is a high-pressure refrigerant, or as in the case of performing a two-stage refrigeration cycle in which carbon dioxide, which is a high-pressure refrigerant, is used in the heat-source-side cycle, the reduction being due to the pressure of the carbon dioxide refrigerant exceeding the critical pressure. It is also possible to reduce the compression strength standards required for the components of the refrigerant circuit 10 in which carbon dioxide, which is a high-pressure refrigerant, is used.

(3) Third Embodiment

FIG. 9 is a schematic configuration diagram of a refrigeration cycle apparatus 1 b according to a third embodiment. FIG. 10 is a functional block configuration diagram of the refrigeration cycle apparatus 1 b according to the third embodiment.

The refrigeration cycle apparatus 1 b is an apparatus used to process a heat load through a vapor-compression refrigeration cycle operation. The refrigeration cycle apparatus 1 b includes a heat-load circuit 90, a refrigerant circuit 10, an outdoor fan 9, and a controller 7.

The heat load to be processed by the refrigeration cycle apparatus 1 b and the heat-load circuit 90 are similar to those according to the first embodiment.

In the present embodiment, as described below, a use heat exchanger 13 includes a first use flow path 13 a through which a first refrigerant or a second refrigerant flowing through the refrigerant circuit 10 passes. Water flowing through a heat-load flow path 13 b of the use heat exchanger 13 exchanges heat with the first refrigerant or second refrigerant flowing through the first use flow path 13 a. As a result, the water is cooled during a cooling operation and is heated during a heating operation.

The refrigerant circuit 10 includes a first compressor 11, a second compressor 21, a first switching mechanism 12, a second switching mechanism 22, the use heat exchanger 13 shared with the heat-load circuit 90, a first expansion valve 15, a second expansion valve 16, a third expansion valve 33, a fourth expansion valve 34, a fifth expansion valve 35, a sixth expansion valve 36, a cascade heat exchanger 17, an outdoor heat exchanger 18, a first receiver 19 a, a second receiver 19 b, a tenth on-off valve 50, an eleventh on-off valve 51, a twelfth on-off valve 52, and a thirteenth on-off valve 53.

The refrigerant circuit 10 is filled with the first refrigerant, which is a low-pressure refrigerant, and the second refrigerant, which is a high-pressure refrigerant, as refrigerants in a substantially separated state. The first refrigerant is a refrigerant having 1 MPa or less at 30° C., and is a refrigerant including, for example, at least one of R1234yf or R1234ze. The first refrigerant may include only R1234yf or may include only R1234ze. The second refrigerant is a refrigerant having 1.5 MPa or more at 30° C. For example, the second refrigerant may include carbon dioxide, or may include only carbon dioxide.

The specific configuration of the first compressor 11 is similar to that according to the first embodiment. A discharge side of the first compressor 11 is connected to a first port of the first switching mechanism 12. A suction side of the first compressor 11 is connected to a second port of the first switching mechanism 12.

In the present embodiment, the first switching mechanism 12 is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port of the first switching mechanism 12 is connected to a branch point P. The branch point P is connected to a flow path extending from the discharge side of the first compressor 11, a flow path extending from a gas refrigerant side of a first cascade flow path 17 a of the cascade heat exchanger 17, and a flow path extending from the first port of the first switching mechanism 12. The second port of the first switching mechanism 12 is connected to the suction side of the first compressor 11. The third port of the first switching mechanism 12 is connected to a flow path extending from the eleventh on-off valve 51. The fourth port of the first switching mechanism 12 is connected to a flow path extending from the tenth on-off valve 50.

The first switching mechanism 12 switches between a state in which the branch point P is connected to the eleventh on-off valve 51 and the suction side of the first compressor 11 is connected to the tenth on-off valve 50 and a state in which the branch point P is connected to the tenth on-off valve 50 and the suction side of the first compressor 11 is connected to the eleventh on-off valve 51.

The tenth on-off valve 50 is an electromagnetic valve controllable to switch between an open state and a closed state. The tenth on-off valve 50 is disposed at a certain point in a flow path connecting the fourth port of the first switching mechanism 12 and a branch point M.

The branch point M is connected to a flow path extending from the tenth on-off valve 50, a flow path extending from the thirteenth on-off valve 53, and a flow path extending from a gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13.

The gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 through which the refrigerant flowing through the refrigerant circuit 10 passes is connected to a flow path extending from the branch point M. A liquid refrigerant side of the first use flow path 13 a is connected to a flow path extending from a branch point A.

At the branch point A, a flow path extending from the liquid refrigerant side of the first use flow path 13 a, a flow path extending to the side of the first expansion valve 15 opposite to a branch point F side, and a flow path extending from the sixth expansion valve 36 are connected.

The first expansion valve 15 is configured as an electronic expansion valve that is adjustable in valve opening degree. In the refrigerant circuit 10, the first expansion valve 15 is disposed at a certain point in a flow path connecting the branch point A and the branch point F.

The branch point F connects a flow path extending from the first expansion valve 15, a flow path extending from the fifth expansion valve 35, and a flow path extending from an upper end of the first receiver 19 a.

The first receiver 19 a is a refrigerant container that stores a refrigerant therein. The first receiver 19 a is disposed at a certain point in a flow path connecting the branch point F and the third expansion valve 33. In the present embodiment, the first receiver 19 a stores the second refrigerant.

The third expansion valve 33 is configured as an electronic expansion valve that is adjustable in valve opening degree. The third expansion valve 33 is disposed at a certain point in a flow path connecting a lower end of the first receiver 19 a and a liquid refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17.

The cascade heat exchanger 17 is a cascade heat exchanger that includes the first cascade flow path 17 a through which one of the first refrigerant and the second refrigerant passes and a second cascade flow path 17 b through which the other of the first refrigerant and the second refrigerant passes, and that exchanges heat between the first refrigerant and the second refrigerant. In the cascade heat exchanger 17, the first cascade flow path 17 a and the second cascade flow path 17 b are independent of each other, and the first refrigerant and the second refrigerant do not mix with each other in the cascade heat exchanger 17. The gas refrigerant side of the first cascade flow path 17 a is connected to a flow path extending from the branch point P. The liquid refrigerant side of the first cascade flow path 17 a is connected to a flow path extending from the third expansion valve 33. A gas refrigerant side of the second cascade flow path 17 b is connected to a flow path extending from a second port of the second switching mechanism 22 and a flow path extending from a suction side of the second compressor 21. A liquid refrigerant side of the second cascade flow path 17 b is connected to a flow path extending from the fourth expansion valve 34.

The specific configuration of the second compressor 21 is similar to that according to the first embodiment. A discharge side of the second compressor 21 is connected to a first port of the second switching mechanism 22. The suction side of the second compressor 21 is connected to the second port of the second switching mechanism 22 and the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17.

In the present embodiment, the second switching mechanism 22 is constituted by a four-way switching valve having four ports including the first port, the second port, a third port, and a fourth port. The first port of the second switching mechanism 22 is connected to the discharge side of the second compressor 21. The second port of the second switching mechanism 22 is connected to the suction side of the second compressor 21 and the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17. The third port of the second switching mechanism 22 is connected to a flow path extending from the thirteenth on-off valve 53. The fourth port of the second switching mechanism 22 is connected to a flow path extending from the twelfth on-off valve 52.

The second switching mechanism 22 switches between a state in which the discharge side of the second compressor 21 is connected to the twelfth on-off valve 52 and the suction side of the second compressor 21 and the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 are connected to the thirteenth on-off valve 53 and a state in which the discharge side of the second compressor 21 is connected to the thirteenth on-off valve 53 and the suction side of the second compressor 21 and the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 are connected to the twelfth on-off valve 52.

The liquid refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 is connected to a flow path extending from the fourth expansion valve 34.

The fourth expansion valve 34 is configured as an electronic expansion valve that is adjustable in valve opening degree. The fourth expansion valve 34 is disposed between the liquid refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 and an upper end of the second receiver 19 b.

The second receiver 19 b is a refrigerant container that stores a refrigerant therein. The second receiver 19 b is disposed at a certain point in a flow path connecting a branch point G and the fourth expansion valve 34. In the present embodiment, the second receiver 19 b stores the first refrigerant.

The branch point G is connected to a flow path extending from a lower end of the second receiver 19 b, a flow path extending from the sixth expansion valve 36, and a flow path extending from the second expansion valve 16.

The second expansion valve 16 is configured as an electronic expansion valve that is adjustable in valve opening degree. The second expansion valve 16 is disposed between the branch point G and a branch point B.

The branch point B is connected to a flow path extending from the second expansion valve 16, a flow path extending from a liquid refrigerant side of the outdoor heat exchanger 18, and a flow path extending from the fifth expansion valve 35.

The outdoor heat exchanger 18 includes a plurality of heat transfer tubes and a plurality of fins joined to the plurality of heat transfer tubes. In the present embodiment, the outdoor heat exchanger 18 is arranged outdoors. A refrigerant flowing through the outdoor heat exchanger 18 exchanges heat with air sent to the outdoor heat exchanger 18. The outdoor heat exchanger 18 is disposed at a certain point in a flow path connecting the branch point B and a branch point N.

The outdoor fan 9 generates an air flow of outdoor air passing through the outdoor heat exchanger 18.

The branch point N is connected to a flow path extending from a gas refrigerant side of the outdoor heat exchanger 18, a flow path extending from the twelfth on-off valve 52, and a flow path extending from the eleventh on-off valve 51.

The eleventh on-off valve 51 is an electromagnetic valve controllable to switch between an open state and a closed state. The eleventh on-off valve 51 is disposed at a certain point in a flow path connecting the third port of the first switching mechanism 12 and the branch point N.

The twelfth on-off valve 52 is an electromagnetic valve controllable to switch between an open state and a closed state. The twelfth on-off valve 52 is disposed at a certain point in a flow path connecting the fourth port of the second switching mechanism 22 and the branch point N.

The thirteenth on-off valve 53 is an electromagnetic valve controllable to switch between an open state and a closed state. The thirteenth on-off valve 53 is disposed at a certain point in a flow path connecting the third port of the second switching mechanism 22 and the branch point M.

The fifth expansion valve 35 is configured as an electronic expansion valve that is adjustable in valve opening degree. The fifth expansion valve 35 is disposed at a certain point in a flow path connecting the branch point F and the branch point B.

The sixth expansion valve 36 is configured as an electronic expansion valve that is adjustable in valve opening degree. The sixth expansion valve 36 is disposed at a certain point in a flow path connecting the branch point A and the branch point G.

The controller 7 controls the operation of the devices included in the heat-load circuit 90 and the refrigerant circuit 10. Specifically, the controller 7 includes a processor serving as a CPU provided for performing control, a memory, and the like.

In the refrigeration cycle apparatus 1 b described above, the controller 7 controls the devices to execute a refrigeration cycle, thereby performing a cooling operation for processing a cooling load in the heat-load heat exchanger 91, a heating operation for processing a heating load in the heat-load heat exchanger 91, a cooling-to-heating transition operation, and a heating-to-cooling transition operation.

(3-1) Cooling Operation

During the cooling operation, as illustrated in FIG. 11 , a two-stage refrigeration cycle operation is performed in which the first refrigerant is used in a heat-source-side refrigeration cycle and the second refrigerant is used in a use-side refrigeration cycle. In FIG. 11 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as an evaporator of the second refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, and the outdoor heat exchanger 18 is caused to function as a condenser of the first refrigerant.

Specifically, in this two-stage refrigeration cycle, all of the eleventh on-off valve 51 and the thirteenth on-off valve 53 are controlled to be in a closed state, and the fifth expansion valve 35 and the sixth expansion valve 36 are controlled to be in a fully closed state to prevent mixing of the first refrigerant and the second refrigerant. The tenth on-off valve 50 and the twelfth on-off valve 52 are controlled to be in an open state. Then, a connection state of the first switching mechanism 12 is switched to a connection state indicated by solid lines in FIG. 11 , a connection state of the second switching mechanism 22 is switched to a connection state indicated by solid lines in FIG. 11 , and the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven. Further, the valve opening degree of the first expansion valve 15 is controlled such that the degree of superheating of the second refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the fourth expansion valve 34 is controlled such that the degree of superheating of the first refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the first refrigerant discharged from the second compressor 21 is sent to the outdoor heat exchanger 18 via the second switching mechanism 22 and the twelfth on-off valve 52. The first refrigerant flowing through the outdoor heat exchanger 18 is condensed by heat exchange with the outdoor air supplied by the outdoor fan 9. The first refrigerant condensed in the outdoor heat exchanger 18 passes through the second expansion valve 16, which is controlled to be in a fully open state. After that, the first refrigerant passes through the branch point G and flows into the second receiver 19 b. The refrigerant having flowed out of the second receiver 19 b is decompressed in the fourth expansion valve 34 and is sent to the second cascade flow path 17 b of the cascade heat exchanger 17. When flowing through the second cascade flow path 17 b of the cascade heat exchanger 17, the first refrigerant is evaporated by heat exchange with the second refrigerant flowing through the first cascade flow path 17 a. The first refrigerant evaporated in the cascade heat exchanger 17 is sucked into the second compressor 21. The second refrigerant discharged from the first compressor 11 passes through the branch point P and is sent to the first cascade flow path 17 a of the cascade heat exchanger 17. When flowing through the first cascade flow path 17 a of the cascade heat exchanger 17, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the second cascade flow path 17 b. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, passes through the third expansion valve 33, which is controlled to be in a fully open state, and flows into the first receiver 19 a. The second refrigerant having flowed out of the first receiver 19 a is decompressed in the first expansion valve 15, passes through the branch point A, and is sent to the first use flow path 13 a of the use heat exchanger 13. The second refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is evaporated by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water cooled by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the cooling load. The second refrigerant evaporated in the first use flow path 13 a of the use heat exchanger 13 is sucked into the first compressor 11 via the tenth on-off valve 50 and the first switching mechanism 12.

(3-2) Cooling-to-Heating Transition Operation

The refrigeration cycle apparatus 1 b performs a cooling-to-heating transition operation including (a3) to (b3) below in this order to make a transition from a cycle state for performing the cooling operation to a cycle state for performing the heating operation.

-   -   (a3) First, the first compressor 11 is operated after the first         expansion valve 15 is controlled to be in a fully closed state         from the state in which the cooling operation is performed.         Here, the second compressor 21 and the like are operated such         that the refrigeration cycle for the cooling operation using the         first refrigerant is performed. As a result, an operation of         recovering the second refrigerant into the first receiver 19 a         from below the first receiver 19 a is performed. This operation         is continued for a predetermined period of time, for example,         until a predetermined sufficient amount of the second         refrigerant is recovered in the first receiver 19 a.     -   (b3) Then, the tenth on-off valve 50 is closed and the first         compressor 11 is stopped after the second refrigerant has been         recovered into the first receiver 19 a by a predetermined amount         or more. After that, the second switching mechanism 22 is         switched to a state in which the discharge side of the second         compressor 21 is connected to the thirteenth on-off valve 53 and         the suction side of the second compressor 21 is connected to the         twelfth on-off valve 52 and the gas refrigerant side of the         second cascade flow path 17 b of the cascade heat exchanger 17.         Further, the twelfth on-off valve 52 and the thirteenth on-off         valve 53 are controlled to be in an open state, the second         expansion valve 16 and the fourth expansion valve 34 are         controlled to be in a fully closed state, and the sixth         expansion valve 36 is controlled to be in an open state. In this         state, the second compressor 21 is operated to heat and expel         the first refrigerant remaining in the outdoor heat exchanger 18         by using the heat of the air obtained from the outdoor fan 9.         Then, the first refrigerant is sucked into the second compressor         21 via the twelfth on-off valve 52 and the second switching         mechanism 22. The first refrigerant remaining in the second         cascade flow path 17 b of the cascade heat exchanger 17 is also         sucked into the second compressor 21. The first refrigerant         discharged from the second compressor 21 is sent to the first         use flow path 13 a of the use heat exchanger 13 via the second         switching mechanism 22, the thirteenth on-off valve 53, and the         branch point M. Further, the first refrigerant condenses when         flowing through the first use flow path 13 a of the use heat         exchanger 13, and flows into the second receiver 19 b via the         branch point A and the sixth expansion valve 36. After this         operation is continued for a predetermined period of time, the         twelfth on-off valve 52 is controlled to be in a closed state,         and the fourth expansion valve 34 is controlled to be in an open         state.

Thus, the cooling-to-heating transition operation is completed.

(3-3) Heating Operation

During the heating operation, as illustrated in FIG. 12 , a two-stage refrigeration cycle is performed in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. In FIG. 12 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as a condenser of the first refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, and the outdoor heat exchanger 18 is caused to function as an evaporator of the second refrigerant.

Specifically, in this two-stage refrigeration cycle, the tenth on-off valve 50 and the twelfth on-off valve 52 are controlled to be in a closed state, and the first expansion valve 15 and the second expansion valve 16 are controlled to be in a fully closed state to prevent mixing of the first refrigerant and the second refrigerant. Then, a connection state of the first switching mechanism 12 is changed to a state indicated by broken lines in FIG. 12 , a connection state of the second switching mechanism 22 is switched to a connection state indicated by broken lines in FIG. 12 , and the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven. Further, the valve opening degree of the fifth expansion valve 35 is controlled such that the degree of superheating of the second refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the fourth expansion valve 34 is controlled such that the degree of superheating of the first refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the second refrigerant discharged from the first compressor 11 is sent to the cascade heat exchanger 17. When flowing through the first cascade flow path 17 a, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the second cascade flow path 17 b. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, is decompressed in the fifth expansion valve 35 via the third expansion valve 33, the first receiver 19 a, and the branch point F. The second refrigerant decompressed in the fifth expansion valve 35 is sent to the outdoor heat exchanger 18 via the branch point B. The second refrigerant is evaporated by heat exchange with the outdoor air supplied by the outdoor fan 9 in the outdoor heat exchanger 18, and is sucked into the first compressor 11 via the branch point N, the eleventh on-off valve 51, and the first switching mechanism 12. The first refrigerant discharged from the second compressor 21 is sent to the first use flow path 13 a of the use heat exchanger 13 via the second switching mechanism 22, the thirteenth on-off valve 53, and the branch point M. The first refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is condensed by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water heated by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the heating load. The first refrigerant condensed in the first use flow path 13 a of the use heat exchanger 13 passes through the branch point A. After that, the first refrigerant passes through the sixth expansion valve 36 and flows into the second receiver 19 b. The first refrigerant having flowed out of the second receiver 19 b is decompressed in the fourth expansion valve 34. The first refrigerant decompressed by the fourth expansion valve 34 is evaporated, when passing through the second cascade flow path 17 b of the cascade heat exchanger 17, by heat exchange with the second refrigerant flowing through the first cascade flow path 17 a. The first refrigerant evaporated in the second cascade flow path 17 b of the cascade heat exchanger 17 is sucked into the second compressor 21.

(3-4) Heating-to-Cooling Transition Operation

The refrigeration cycle apparatus 1 b performs a heating-to-cooling transition operation including (a4) to (c4) below in this order to make a transition from a cycle state for performing the heating operation to a cycle state for performing the cooling operation.

-   -   (a4) First, the fifth expansion valve 35 is controlled to be in         a fully closed state from the state in which the heating         operation is performed, and the first compressor 11 is operated.         Here, the second compressor 21 and the like are operated such         that the use-side refrigeration cycle for the heating operation         using the first refrigerant is maintained. Accordingly, an         operation of, while sucking the second refrigerant in the         outdoor heat exchanger 18 into the first compressor 11, causing         the second refrigerant discharged from the first compressor 11         to radiate heat in the first cascade flow path 17 a of the         cascade heat exchanger 17, causing the second refrigerant to         flow into the first receiver 19 a, and recovering the second         refrigerant into the first receiver 19 a is performed. This         operation is continued for a predetermined period of time, for         example, until a predetermined sufficient amount of the second         refrigerant is recovered in the first receiver 19 a.     -   (b4) Then, the eleventh on-off valve 51 is closed and the first         compressor 11 is stopped after the second refrigerant has been         recovered into the first receiver 19 a by a predetermined amount         or more. After that, the second switching mechanism 22 is         switched to a state in which the discharge side of the second         compressor 21 is connected to the twelfth on-off valve 52 and         the suction side of the second compressor 21 is connected to the         thirteenth on-off valve 53 and the gas refrigerant side of the         second cascade flow path 17 b of the cascade heat exchanger 17.         Then, the sixth expansion valve 36 and the fourth expansion         valve 34 are controlled to be in a fully closed state, and the         second expansion valve 16 is controlled to be in a fully open         state. In this state, the second compressor 21 is operated to         suck the first refrigerant remaining in and around the first use         flow path 13 a of the use heat exchanger 13 into the second         compressor 21 and discharge the first refrigerant from the         second compressor 21. As a result, the first refrigerant is         condensed in the outdoor heat exchanger 18. The first         refrigerant condensed in the outdoor heat exchanger 18 begins to         accumulate in the second receiver 19 b. Then, this operation is         continued for a predetermined period of time.     -   (c4) Then, after a predetermined amount or more of the first         refrigerant has accumulated in the second receiver 19 b, the         thirteenth on-off valve 53 is controlled to be in a closed         state. Then, the first switching mechanism 12 is switched to a         state in which the discharge side of the first compressor 11 is         connected to the eleventh on-off valve 51 and the suction side         of the first compressor 11 is connected to the tenth on-off         valve 50, the tenth on-off valve 50 is controlled to be in an         open state, and the first expansion valve 15 is controlled to         have a predetermined valve opening degree.

Thus, the heating-to-cooling transition operation is completed.

(3-5) Features of Third Embodiment

In the refrigeration cycle apparatus 1 b according to the third embodiment, the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP) and the second refrigerant having a sufficiently low ozone depletion potential (ODP) and a sufficiently low global warming potential (GWP). Thus, global environmental deterioration can be reduced.

In addition, even when the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP), the two-stage refrigeration cycle in which the second refrigerant, which is a high-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the first refrigerant, which is a low-pressure refrigerant, is used in the use-side refrigeration cycle is performed as the heating operation. This makes it easier to secure heating operation capacity than a single-stage refrigeration cycle using the first refrigerant, which is a low-pressure refrigerant.

Further, the refrigerant circuit 10 uses carbon dioxide as the second refrigerant. However, during the cooling operation, a single-stage refrigeration cycle using the second refrigerant is not performed, nor is performed a two-stage refrigeration cycle in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. Instead of this, a two-stage refrigeration cycle in which the first refrigerant, which is a low-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the second refrigerant, which is a high-pressure refrigerant, is used in the use-side refrigeration cycle is performed. This makes it possible to perform the cooling operation without causing a reduction in COP, as in the case of performing a single-stage refrigeration cycle using a carbon dioxide refrigerant, which is a high-pressure refrigerant, or as in the case of performing a two-stage refrigeration cycle in which carbon dioxide, which is a high-pressure refrigerant, is used in the heat-source-side cycle, the reduction being due to the pressure of the carbon dioxide refrigerant exceeding the critical pressure. It is also possible to reduce the compression strength standards required for the components of the refrigerant circuit 10 in which carbon dioxide, which is a high-pressure refrigerant, is used.

In the refrigeration cycle apparatus 1 b according to the third embodiment, furthermore, the first refrigerant and the second refrigerant can be collected by using the first receiver 19 a and the second receiver 19 b used in the heat-source-side refrigeration cycle and the use-side refrigeration cycle. This eliminates the need to separately secure the refrigerant container 19 as described in the second embodiment, which is not used in the heat-source-side refrigeration cycle or the use-side refrigeration cycle.

(4) Fourth Embodiment

FIG. 13 is a schematic configuration diagram of a refrigeration cycle apparatus 1 c according to a fourth embodiment. FIG. 14 is a functional block configuration diagram of the refrigeration cycle apparatus 1 c according to the fourth embodiment.

The refrigeration cycle apparatus 1 c is an apparatus used to process a heat load through a vapor-compression refrigeration cycle operation. The refrigeration cycle apparatus 1 c includes a heat-load circuit 90, a refrigerant circuit 10, an outdoor fan 9, and a controller 7.

The heat load to be processed by the refrigeration cycle apparatus 1 c and the heat-load circuit 90 are similar to those according to the first embodiment.

In the present embodiment, as described below, a use heat exchanger 13 includes a first use flow path 13 a through which a first refrigerant or a second refrigerant flowing through the refrigerant circuit 10 passes. Water flowing through a heat-load flow path 13 b of the use heat exchanger 13 exchanges heat with the first refrigerant or second refrigerant flowing through the first use flow path 13 a. As a result, the water is cooled during a cooling operation and is heated during a heating operation.

The refrigerant circuit 10 includes a first compressor 11, a second compressor 21, a first switching mechanism 12, a second switching mechanism 22, the use heat exchanger 13 shared with the heat-load circuit 90, a first expansion valve 15, a second expansion valve 16, a third expansion valve 33, a fourth expansion valve 34, a fifth expansion valve 35, a sixth expansion valve 36, a cascade heat exchanger 17, an outdoor heat exchanger 18, a first receiver 19 a, a second receiver 19 b, a fourteenth on-off valve 54, a fifteenth on-off valve 55, a sixteenth on-off valve 56, and a seventeenth on-off valve 57.

The refrigerant circuit 10 is filled with the first refrigerant, which is a low-pressure refrigerant, and the second refrigerant, which is a high-pressure refrigerant, as refrigerants in a substantially separated state. The first refrigerant is a refrigerant having 1 MPa or less at 30° C. and is a refrigerant including, for example, at least one of R1234yf or R1234ze. The first refrigerant may include only R1234yf or may include only R1234ze. The second refrigerant is a refrigerant having 1.5 MPa or more at 30° C. For example, the second refrigerant may include carbon dioxide, or may include only carbon dioxide.

The specific configuration of the first compressor 11 is similar to that according to the first embodiment. A discharge side of the first compressor 11 is connected to a switching valve 12 c, a switching valve 12 d, and a switching valve 12 e of the first switching mechanism 12. A suction side of the first compressor 11 is connected to different ports of the switching valve 12 c, the switching valve 12 d, and the switching valve 12 e of the first switching mechanism 12.

The first switching mechanism 12 includes the switching valve 12 c, the switching valve 12 d, and the switching valve 12 e, which are disposed in parallel to each other on the discharge side of the first compressor 11. In the present embodiment, the switching valve 12 c, the switching valve 12 d, and the switching valve 12 e are each constituted by a three-way valve. The switching valve 12 c switches between a state in which the discharge side of the first compressor 11 is connected to the fourteenth on-off valve 54 and a state in which the suction side of the first compressor 11 is connected to the fourteenth on-off valve 54. The switching valve 12 d switches between a state in which the discharge side of the first compressor 11 is connected to a gas refrigerant side of a first cascade flow path 17 a of the cascade heat exchanger 17 and a state in which the suction side of the first compressor 11 is connected to the gas refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17. The switching valve 12 e switches between a state in which the discharge side of the first compressor 11 is connected to the sixteenth on-off valve 56 and a state in which the suction side of the first compressor 11 is connected to the sixteenth on-off valve 56.

The fourteenth on-off valve 54 is an electromagnetic valve controllable to switch between an open state and a closed state. The fourteenth on-off valve 54 is disposed at a certain point in a flow path connecting the switching valve 12 c of the first switching mechanism 12 and a branch point M.

The branch point M is connected to a flow path extending from the fourteenth on-off valve 54, a flow path extending from the fifteenth on-off valve 55, and a flow path extending from a gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13.

The gas refrigerant side of the first use flow path 13 a of the use heat exchanger 13 through which the refrigerant flowing through the refrigerant circuit 10 passes is connected to a flow path extending from the branch point M. A liquid refrigerant side of the first use flow path 13 a is connected to a flow path extending from a branch point A.

At the branch point A, a flow path extending from the liquid refrigerant side of the first use flow path 13 a, a flow path extending to the side of the first expansion valve 15 opposite to a branch point F side, and a flow path extending from the sixth expansion valve 36 are connected.

The first expansion valve 15 is configured as an electronic expansion valve that is adjustable in valve opening degree. In the refrigerant circuit 10, the first expansion valve 15 is disposed at a certain point in a flow path connecting the branch point A and the branch point F.

The branch point F connects a flow path extending from the first expansion valve 15, a flow path extending from the fifth expansion valve 35, and a flow path extending from an upper end of the first receiver 19 a.

The first receiver 19 a is a refrigerant container that stores a refrigerant therein. The first receiver 19 a is disposed at a certain point in a flow path connecting the branch point F and the third expansion valve 33. In the present embodiment, the first receiver 19 a stores the second refrigerant.

The third expansion valve 33 is configured as an electronic expansion valve that is adjustable in valve opening degree. The third expansion valve 33 is disposed at a certain point in a flow path connecting a lower end of the first receiver 19 a and a liquid refrigerant side of the first cascade flow path 17 a of the cascade heat exchanger 17.

The cascade heat exchanger 17 is a cascade heat exchanger that includes the first cascade flow path 17 a through which one of the first refrigerant and the second refrigerant passes and a second cascade flow path 17 b through which the other of the first refrigerant and the second refrigerant passes, and that exchanges heat between the first refrigerant and the second refrigerant. In the cascade heat exchanger 17, the first cascade flow path 17 a and the second cascade flow path 17 b are independent of each other, and the first refrigerant and the second refrigerant do not mix with each other in the cascade heat exchanger 17. The gas refrigerant side of the first cascade flow path 17 a is connected to a flow path extending from the switching valve 12 d of the first switching mechanism 12. The liquid refrigerant side of the first cascade flow path 17 a is connected to a flow path extending from the third expansion valve 33. A gas refrigerant side of the second cascade flow path 17 b is connected to a flow path extending from a switching valve 22 d of the second switching mechanism 22. A liquid refrigerant side of the second cascade flow path 17 b is connected to a flow path extending from the fourth expansion valve 34.

The specific configuration of the second compressor 21 is similar to that according to the first embodiment. A discharge side of the second compressor 21 is connected to a switching valve 22 c, the switching valve 22 d, and a switching valve 22 e of the second switching mechanism 22. A suction side of the second compressor 21 is connected to different ports of the switching valve 22 c, the switching valve 22 d, and the switching valve 22 e of the second switching mechanism 22.

The second switching mechanism 22 includes the switching valve 22 c, the switching valve 22 d, and the switching valve 22 e, which are disposed in parallel to each other on the discharge side of the second compressor 21. In the present embodiment, the switching valve 22 c, the switching valve 22 d, and the switching valve 22 e are each constituted by a three-way valve. The switching valve 22 c switches between a state in which the discharge side of the second compressor 21 is connected to the fifteenth on-off valve 55 and a state in which the suction side of the second compressor 21 is connected to the fifteenth on-off valve 55. The switching valve 22 d switches between a state in which the discharge side of the second compressor 21 is connected to the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 and a state in which the suction side of the second compressor 21 is connected to the gas refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17. The switching valve 22 e switches between a state in which the discharge side of the second compressor 21 is connected to the seventeenth on-off valve 57 and a state in which the suction side of the second compressor 21 is connected to the seventeenth on-off valve 57.

The liquid refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 is connected to a flow path extending from the fourth expansion valve 34.

The fourth expansion valve 34 is configured as an electronic expansion valve that is adjustable in valve opening degree. The fourth expansion valve 34 is disposed between the liquid refrigerant side of the second cascade flow path 17 b of the cascade heat exchanger 17 and an upper end of the second receiver 19 b.

The second receiver 19 b is a refrigerant container that stores a refrigerant therein. The second receiver 19 b is disposed at a certain point in a flow path connecting a branch point G and the fourth expansion valve 34. In the present embodiment, the second receiver 19 b stores the first refrigerant.

The branch point G is connected to a flow path extending from a lower end of the second receiver 19 b, a flow path extending from the sixth expansion valve 36, and a flow path extending from the second expansion valve 16.

The second expansion valve 16 is configured as an electronic expansion valve that is adjustable in valve opening degree. The second expansion valve 16 is disposed between the branch point G and a branch point B.

The branch point B is connected to a flow path extending from the second expansion valve 16, a flow path extending from a liquid refrigerant side of the outdoor heat exchanger 18, and a flow path extending from the fifth expansion valve 35.

The outdoor heat exchanger 18 includes a plurality of heat transfer tubes and a plurality of fins joined to the plurality of heat transfer tubes. In the present embodiment, the outdoor heat exchanger 18 is arranged outdoors. A refrigerant flowing through the outdoor heat exchanger 18 exchanges heat with air sent to the outdoor heat exchanger 18. The outdoor heat exchanger 18 is disposed at a certain point in a flow path connecting the branch point B and a branch point N.

The outdoor fan 9 generates an air flow of outdoor air passing through the outdoor heat exchanger 18.

The branch point N is connected to a flow path extending from a gas refrigerant side of the outdoor heat exchanger 18, a flow path extending from the sixteenth on-off valve 56, and a flow path extending from the seventeenth on-off valve 57.

The fifteenth on-off valve 55 is an electromagnetic valve controllable to switch between an open state and a closed state. The fifteenth on-off valve 55 is disposed at a certain point in a flow path connecting the switching valve 22 c of the second switching mechanism 22 and a branch point M.

The sixteenth on-off valve 56 is an electromagnetic valve controllable to switch between an open state and a closed state. The sixteenth on-off valve 56 is disposed at a certain point in a flow path connecting the switching valve 12 e of the first switching mechanism 12 and the branch point N.

The seventeenth on-off valve 57 is an electromagnetic valve controllable to switch between an open state and a closed state. The seventeenth on-off valve 57 is disposed at a certain point in a flow path connecting the switching valve 22 e of the second switching mechanism 22 and the branch point N.

The fifth expansion valve 35 is configured as an electronic expansion valve that is adjustable in valve opening degree. The fifth expansion valve 35 is disposed at a certain point in a flow path connecting the branch point F and the branch point B.

The sixth expansion valve 36 is configured as an electronic expansion valve that is adjustable in valve opening degree. The sixth expansion valve 36 is disposed at a certain point in a flow path connecting the branch point A and the branch point G.

The controller 7 controls the operation of the devices included in the heat-load circuit 90 and the refrigerant circuit 10. Specifically, the controller 7 includes a processor serving as a CPU provided for performing control, a memory, and the like.

In the refrigeration cycle apparatus 1 c described above, the controller 7 controls the devices to execute a refrigeration cycle, thereby performing a cooling operation for processing a cooling load in the heat-load heat exchanger 91, a heating operation for processing a heating load in the heat-load heat exchanger 91, a cooling-to-heating transition operation, and a heating-to-cooling transition operation.

(4-1) Cooling Operation

During the cooling operation, as illustrated in FIG. 15 , a two-stage refrigeration cycle operation is performed in which the first refrigerant is used in a heat-source-side refrigeration cycle and the second refrigerant is used in a use-side refrigeration cycle. In FIG. 15 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as an evaporator of the second refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, and the outdoor heat exchanger 18 is caused to function as a condenser of the first refrigerant.

Specifically, in this two-stage refrigeration cycle, all of the fifteenth on-off valve 55 and the sixteenth on-off valve 56 are controlled to be in a closed state, and the fifth expansion valve 35 and the sixth expansion valve 36 are controlled to be in a fully closed state to prevent mixing of the first refrigerant and the second refrigerant. The fourteenth on-off valve 54 and the seventeenth on-off valve 57 are controlled to be in an open state. Then, a connection state of the first switching mechanism 12 is switched to a connection state indicated by solid lines in FIG. 15 , a connection state of the second switching mechanism 22 is switched to a connection state indicated by solid lines in FIG. 15 , and the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven. Further, the valve opening degree of the first expansion valve 15 is controlled such that the degree of superheating of the second refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the fourth expansion valve 34 is controlled such that the degree of superheating of the first refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the first refrigerant discharged from the second compressor 21 is sent to the outdoor heat exchanger 18 via the switching valve 22 e of the second switching mechanism 22, the seventeenth on-off valve 57, and the branch point N. The first refrigerant flowing through the outdoor heat exchanger 18 is condensed by heat exchange with the outdoor air supplied by the outdoor fan 9. The first refrigerant condensed in the outdoor heat exchanger 18 passes through the second expansion valve 16, which is controlled to be in a fully open state. After that, the first refrigerant passes through the branch point G and flows into the second receiver 19 b. The refrigerant having flowed out of the second receiver 19 b is decompressed in the fourth expansion valve 34 and is sent to the second cascade flow path 17 b of the cascade heat exchanger 17. When flowing through the second cascade flow path 17 b of the cascade heat exchanger 17, the first refrigerant is evaporated by heat exchange with the second refrigerant flowing through the first cascade flow path 17 a. The first refrigerant evaporated in the cascade heat exchanger 17 is sucked into the second compressor 21 via the switching valve 22 d of the second switching mechanism 22. The second refrigerant discharged from the first compressor 11 is sent to the first cascade flow path 17 a of the cascade heat exchanger 17 via the switching valve 12 d of the first switching mechanism 12. When flowing through the first cascade flow path 17 a of the cascade heat exchanger 17, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the second cascade flow path 17 b. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, passes through the third expansion valve 33, which is controlled to be in a fully open state, and flows into the first receiver 19 a. The second refrigerant having flowed out of the first receiver 19 a is decompressed in the first expansion valve 15, passes through the branch point A, and is sent to the first use flow path 13 a of the use heat exchanger 13. The second refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is evaporated by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water cooled by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the cooling load. The second refrigerant evaporated in the first use flow path 13 a of the use heat exchanger 13 is sucked into the first compressor 11 via the fourteenth on-off valve 54 and the switching valve 12 c of the first switching mechanism 12.

(4-2) Cooling-to-Heating Transition Operation

The refrigeration cycle apparatus 1 c performs a cooling-to-heating transition operation including (a5) to (b5) below in this order to make a transition from a cycle state for performing the cooling operation to a cycle state for performing the heating operation.

-   -   (a5) First, the first compressor 11 is operated after the first         expansion valve 15 is controlled to be in a fully closed state         from the state in which the cooling operation is performed.         Here, the second compressor 21 and the like are operated such         that the refrigeration cycle for the cooling operation using the         first refrigerant is performed. As a result, an operation of         recovering the second refrigerant into the first receiver 19 a         from below the first receiver 19 a is performed. This operation         is continued for a predetermined period of time, for example,         until a predetermined sufficient amount of the second         refrigerant is recovered in the first receiver 19 a.     -   (b5) Then, the fourteenth on-off valve 54 is closed and the         first compressor 11 is stopped after the second refrigerant has         been recovered into the first receiver 19 a by a predetermined         amount or more. After that, the switching valve 22 c of the         second switching mechanism 22 is switched to a state in which         the discharge side of the second compressor 21 is connected to         the fifteenth on-off valve 55, the switching valve 22 e of the         second switching mechanism 22 is switched to a state in which         the suction side of the second compressor 21 is connected to the         seventeenth on-off valve 57, and the switching valve 22 d of the         second switching mechanism 22 is maintained in a state in which         the suction side of the second compressor 21 is connected to the         gas refrigerant side of the second cascade flow path 17 b of the         cascade heat exchanger 17. Further, the fifteenth on-off valve         55 is controlled to be in an open state, the second expansion         valve 16 and the fourth expansion valve 34 are controlled to be         in a fully closed state, and the sixth expansion valve 36 is         controlled to be in an open state. In this state, the second         compressor 21 is operated to heat and expel the first         refrigerant remaining in the outdoor heat exchanger 18 by using         the heat of the air obtained from the outdoor fan 9. Then, the         first refrigerant is sucked into the second compressor 21 via         the seventeenth on-off valve 57 and the switching valve 22 e of         the second switching mechanism 22. The first refrigerant         remaining in the second cascade flow path 17 b of the cascade         heat exchanger 17 is also sucked into the second compressor 21         via the switching valve 22 d of the second switching mechanism         22. The first refrigerant discharged from the second compressor         21 is sent to the first use flow path 13 a of the use heat         exchanger 13 via the switching valve 22 c of the second         switching mechanism 22, the fifteenth on-off valve 55, and the         branch point M. Further, the first refrigerant condenses when         flowing through the first use flow path 13 a of the use heat         exchanger 13, and flows into the second receiver 19 b via the         branch point A and the sixth expansion valve 36. After this         operation is continued for a predetermined period of time, the         seventeenth on-off valve 57 is controlled to be in a closed         state, and the fourth expansion valve 34 is controlled to be in         an open state.

Thus, the cooling-to-heating transition operation is completed.

(4-3) Heating Operation

During the heating operation, as illustrated in FIG. 16 , a two-stage refrigeration cycle is performed in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. In FIG. 16 , a single-headed arrow indicates a flow path through which the first refrigerant flows, and a double-headed arrow indicates a flow path through which the second refrigerant flows. In this two-stage refrigeration cycle, the use heat exchanger 13 is caused to function as a condenser of the first refrigerant, the cascade heat exchanger 17 is caused to function as an evaporator of the first refrigerant, the cascade heat exchanger 17 is caused to function as a radiator of the second refrigerant, and the outdoor heat exchanger 18 is caused to function as an evaporator of the second refrigerant.

Specifically, in this two-stage refrigeration cycle, the fourteenth on-off valve 54 and the seventeenth on-off valve 57 are controlled to be in a closed state, and the first expansion valve 15 and the second expansion valve 16 are controlled to be in a fully closed state to prevent mixing of the first refrigerant and the second refrigerant. Then, a connection state of the switching valve 12 d and the switching valve 12 c of the first switching mechanism 12 is changed to a state indicated by solid lines in FIG. 16 , a connection state of the switching valve 12 e of the first switching mechanism 12 is changed to a state indicated by a broken line in FIG. 16 , a connection state of the switching valve 22 d and the switching valve 22 e of the second switching mechanism 22 is changed to a connection state indicated by solid lines in FIG. 16 , a connection state of the switching valve 22 c of the second switching mechanism 22 is switched to a connection state indicated by a broken line in FIG. 16 , and the pump 92, the first compressor 11, the second compressor 21, and the outdoor fan 9 are driven. Further, the valve opening degree of the fifth expansion valve 35 is controlled such that the degree of superheating of the second refrigerant to be sucked into the first compressor 11 satisfies a predetermined condition, and the valve opening degree of the fourth expansion valve 34 is controlled such that the degree of superheating of the first refrigerant to be sucked into the second compressor 21 satisfies a predetermined condition.

Accordingly, the second refrigerant discharged from the first compressor 11 is sent to the cascade heat exchanger 17 via the switching valve 12 d of the first switching mechanism 12. When flowing through the first cascade flow path 17 a, the second refrigerant radiates heat by heat exchange with the first refrigerant flowing through the second cascade flow path 17 b. The second refrigerant, which has radiated heat in the cascade heat exchanger 17, is decompressed in the fifth expansion valve 35 via the third expansion valve 33, the first receiver 19 a, and the branch point F. The second refrigerant decompressed in the fifth expansion valve 35 is sent to the outdoor heat exchanger 18 via the branch point B. The second refrigerant is evaporated by heat exchange with the outdoor air supplied by the outdoor fan 9 in the outdoor heat exchanger 18, and is sucked into the first compressor 11 via the branch point N, the sixteenth on-off valve 56, and the switching valve 12 e of the first switching mechanism 12. The first refrigerant discharged from the second compressor 21 is sent to the first use flow path 13 a of the use heat exchanger 13 via the switching valve 22 c of the second switching mechanism 22, the fifteenth on-off valve 55, and the branch point M. The first refrigerant flowing through the first use flow path 13 a of the use heat exchanger 13 is condensed by heat exchange with the water flowing through the heat-load flow path 13 b of the use heat exchanger 13 included in the heat-load circuit 90. The water heated by this heat exchange is sent to the heat-load heat exchanger 91 in the heat-load circuit 90 to process the heating load. The first refrigerant condensed in the first use flow path 13 a of the use heat exchanger 13 passes through the branch point A. After that, the first refrigerant passes through the sixth expansion valve 36 and flows into the second receiver 19 b. The first refrigerant having flowed out of the second receiver 19 b is decompressed in the fourth expansion valve 34. The first refrigerant decompressed by the fourth expansion valve 34 is evaporated, when passing through the second cascade flow path 17 b of the cascade heat exchanger 17, by heat exchange with the second refrigerant flowing through the first cascade flow path 17 a. The first refrigerant evaporated in the second cascade flow path 17 b of the cascade heat exchanger 17 is sucked into the second compressor 21 via the switching valve 22 d of the second switching mechanism 22.

(4-4) Heating-to-Cooling Transition Operation

The refrigeration cycle apparatus 1 c performs a heating-to-cooling transition operation including (a6) to (c6) below in this order to make a transition from a cycle state for performing the heating operation to a cycle state for performing the cooling operation.

-   -   (a6) First, the fifth expansion valve 35 is controlled to be in         a fully closed state from the state in which the heating         operation is performed, and the first compressor 11 is operated.         Here, the second compressor 21 and the like are operated such         that the use-side refrigeration cycle for the heating operation         using the first refrigerant is maintained. Accordingly, an         operation of, while sucking the second refrigerant in the         outdoor heat exchanger 18 into the first compressor 11, causing         the second refrigerant discharged from the first compressor 11         to radiate heat in the first cascade flow path 17 a of the         cascade heat exchanger 17, causing the second refrigerant to         flow into the first receiver 19 a, and recovering the second         refrigerant into the first receiver 19 a is performed. This         operation is continued for a predetermined period of time, for         example, until a predetermined sufficient amount of the second         refrigerant is recovered in the first receiver 19 a.     -   (b6) Then, the sixteenth on-off valve 56 is closed and the first         compressor 11 is stopped after the second refrigerant has been         recovered into the first receiver 19 a by a predetermined amount         or more. After that, the switching valve 22 c of the second         switching mechanism 22 is switched to a state in which the         suction side of the second compressor 21 is connected to the         fifteenth on-off valve 55, the switching valve 22 e of the         second switching mechanism 22 is switched to a state in which         the discharge side of the second compressor 21 is connected to         the seventeenth on-off valve 57, and the switching valve 22 d of         the second switching mechanism 22 is maintained in a state in         which the suction side of the second compressor 21 is connected         to the gas refrigerant side of the second cascade flow path 17 b         of the cascade heat exchanger 17. Then, the fourth expansion         valve 34 and the sixth expansion valve 36 are controlled to be         in a fully closed state, the second expansion valve 16 is         controlled to be in a fully open state, and the seventeenth         on-off valve 57 is controlled to be in an open state. In this         state, the second compressor 21 is operated to suck the first         refrigerant remaining in and around the first use flow path 13 a         of the use heat exchanger 13 into the second compressor 21 via         the branch point M, the fifteenth on-off valve 55, and the         switching valve 22 c of the second switching mechanism 22. Then,         the first refrigerant discharged from the second compressor 21         is sent to the outdoor heat exchanger 18 via the switching valve         22 e of the second switching mechanism 22, the seventeenth         on-off valve 57, and the branch point N. The first refrigerant,         which has exchanged heat with the air sent by the outdoor fan 9         in the outdoor heat exchanger 18, is condensed, passes through         the branch point B, the second expansion valve 16, and the         branch point G, and begins to accumulate in the second receiver         19 b. Then, this operation is continued for a predetermined         period of time.     -   (c6) Then, after a predetermined amount or more of the first         refrigerant has accumulated in the second receiver 19 b, the         fifteenth on-off valve 55 is controlled to be in a closed state.         Further, the fourteenth on-off valve 54 is controlled to be in         an open state, and the first expansion valve 15 is controlled to         have a predetermined valve opening degree. Then, the switching         valve 12 c of the first switching mechanism 12 is switched to a         state in which the suction side of the first compressor 11 is         connected to the fourteenth on-off valve 54, the switching valve         12 e of the first switching mechanism 12 is switched to a state         in which the discharge side of the first compressor 11 is         connected to the sixteenth on-off valve 56, and the switching         valve 12 d of the first switching mechanism 12 is switched to a         state in which the discharge side of the first compressor 11 and         the gas refrigerant side of the first cascade flow path 17 a is         connected to the cascade heat exchanger 17 is maintained.

Thus, the heating-to-cooling transition operation is completed.

(4-5) Features of Fourth Embodiment

In the refrigeration cycle apparatus 1 c according to the fourth embodiment, the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP) and the second refrigerant having a sufficiently low ozone depletion potential (ODP) and a sufficiently low global warming potential (GWP). Thus, global environmental deterioration can be reduced.

In addition, even when the refrigerant circuit 10 uses the first refrigerant having a sufficiently low global warming potential (GWP), the two-stage refrigeration cycle in which the second refrigerant, which is a high-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the first refrigerant, which is a low-pressure refrigerant, is used in the use-side refrigeration cycle is performed as the heating operation. This makes it easier to secure heating operation capacity than a single-stage refrigeration cycle using the first refrigerant, which is a low-pressure refrigerant.

Further, the refrigerant circuit 10 uses carbon dioxide as the second refrigerant. However, during the cooling operation, a single-stage refrigeration cycle using the second refrigerant is not performed, nor is performed a two-stage refrigeration cycle in which the second refrigerant is used in the heat-source-side refrigeration cycle and the first refrigerant is used in the use-side refrigeration cycle. Instead of this, a two-stage refrigeration cycle in which the first refrigerant, which is a low-pressure refrigerant, is used in the heat-source-side refrigeration cycle and the second refrigerant, which is a high-pressure refrigerant, is used in the use-side refrigeration cycle is performed. This makes it possible to perform the cooling operation without causing a reduction in COP, as in the case of performing a single-stage refrigeration cycle using a carbon dioxide refrigerant, which is a high-pressure refrigerant, or as in the case of performing a two-stage refrigeration cycle in which carbon dioxide, which is a high-pressure refrigerant, is used in the heat-source-side cycle, the reduction being due to the pressure of the carbon dioxide refrigerant exceeding the critical pressure. It is also possible to reduce the compression strength standards required for the components of the refrigerant circuit 10 in which carbon dioxide, which is a high-pressure refrigerant, is used.

In the refrigeration cycle apparatus 1 c according to the fourth embodiment, furthermore, the first refrigerant and the second refrigerant can be collected by using the first receiver 19 a and the second receiver 19 b used in the heat-source-side refrigeration cycle and the use-side refrigeration cycle. This eliminates the need to separately secure the refrigerant container 19 as described in the second embodiment, which is not used in the heat-source-side refrigeration cycle or the use-side refrigeration cycle.

(5) Other Embodiments (5-1) Other Embodiment A

In the embodiments described above, basically, the first refrigerant and the second refrigerant are circulated without mixing each other. However, various operations performed in the refrigerant circuit 10 may cause a flow of the second refrigerant to a location where the first refrigerant has flowed, and cause a flow of the first refrigerant to a location where the second refrigerant has flowed. In consequence, the first refrigerant and the second refrigerant may sometimes be slightly mixed with each other.

The first refrigerant and the second refrigerant are of different refrigerant types. As a result of mixing of these refrigerants, a non-azeotropic refrigerant mixture flows. In a heat exchanger that functions as an evaporator, the non-azeotropic refrigerant mixture has a temperature gradient such that the refrigerant temperature on the upstream side at the start of evaporation is different from the refrigerant temperature on the downstream side at the end of evaporation. In a heat exchanger that functions as a condenser, the non-azeotropic refrigerant mixture has a temperature gradient such that the refrigerant temperature on the upstream side at the start of condensation is different from the refrigerant temperature on the downstream side at the end of condensation.

Accordingly, the controller 7 may evaluate that the first refrigerant and the second refrigerant are mixed with each other if the difference between the evaporation temperature of the refrigerant at a predetermined upstream position and the evaporation temperature of the refrigerant at a predetermined downstream position in the heat exchanger that functions as an evaporator is equal to or greater than a predetermined value. The controller 7 may evaluate that the first refrigerant and the second refrigerant are mixed with each other if the difference between the condensation temperature of the refrigerant at a predetermined upstream position and the condensation temperature of the refrigerant at a predetermined downstream position in the heat exchanger that functions as a condenser is equal to or greater than a predetermined value. The detection of each temperature is not limited. These temperatures can be detected with temperature sensors disposed at predetermined upstream and downstream locations in the heat exchanger.

The controller 7 may evaluate that the first refrigerant and the second refrigerant are mixed with each other when the concentration of one of the refrigerants is 90 wt % or less, 95 wt % or less, or 98 wt % or less.

In addition, when the controller 7 evaluates that the first refrigerant and the second refrigerant are mixed with each other, the controller 7 may display and output the evaluation result on a display (not illustrated) to provide a notification.

(5-2) Other Embodiment B

As described in the other embodiment A described above, in some cases, the first refrigerant and the second refrigerant are mixed with each other.

Accordingly, the refrigeration cycle apparatus may be configured to perform a separation process for separating the first refrigerant and the second refrigerant from each other when, as described in the other embodiment A described above, it is evaluated that the first refrigerant and the second refrigerant are mixed with each other, when the cooling operation and the heating operation are switched, or when the cooling operation and the heating operation are switched a predetermined number of times.

The separation process is not limited. For example, the refrigerant container 19, the first receiver 19 a, and the second receiver 19 b may be provided with an adsorbent that selectively adsorbs the first refrigerant or the second refrigerant. Examples of the adsorbent may include, but not limited to, a metal-organic framework (MOF).

Further, the refrigeration cycle apparatus may be capable of performing an operation of distilling the first refrigerant or an operation of distilling the second refrigerant.

(5-3) Others

The outdoor heat exchanger is not limited. For example, the refrigerant flowing through the outdoor heat exchanger may exchange heat with air.

The use heat exchanger is preferably a heat exchanger that processes a heat load. The refrigerant flowing through the use heat exchanger may exchange heat with air, or may exchange heat with a fluid such as brine or water.

The state of mixing of the first refrigerant and the second refrigerant to be detected is not limited. For example, it may be detected that the weight percentage of the first refrigerant in the fluid becomes 90% or less or 95% or less, or it may be detected that the weight percentage of the second refrigerant in the fluid becomes 90% or less or 95% or less.

A specific method of the detection is not limited. For example, the detection may be performed based on an increase in the degree of change in the temperature of the refrigerant flowing through the heat exchanger that functions as an evaporator due to an increase in mixing ratio.

The refrigeration cycle apparatus may provide a notification of a result of the detection.

The method of separating the first refrigerant and the second refrigerant from each other is not limited, and a known separation method can be used. For example, adsorbents that adsorb the first refrigerant and the second refrigerant to different degrees may be used, and the refrigerant having higher adsorption efficiency may be separated. Alternatively, the separation may be performed by repeating an operation of separating the refrigerant having a higher purity phase of the gas-phase refrigerant and the liquid-phase refrigerant at a location in a gas-liquid two-phase state. The separation described above may be performed as an operation of the refrigeration cycle apparatus.

The first refrigerant may include only R1234yf or may include only R1234ze.

The second refrigerant may include only carbon dioxide.

<Supplementary Note>

While embodiments of the present disclosure have been described, it will be understood that various changes may be made in form and details without departing from the spirit and scope of the present disclosure as defined in the claims.

REFERENCE SIGNS LIST

-   -   1, 1 a, 1 b, 1 c refrigeration cycle apparatus     -   12 first switching mechanism     -   13 use heat exchanger     -   13 a first use flow path     -   13 b heat-load flow path     -   14 third use expansion valve     -   15 first expansion valve     -   16 second expansion valve     -   17 cascade heat exchanger     -   17 a first cascade flow path     -   17 b second cascade flow path     -   18 outdoor heat exchanger     -   19 refrigerant container (second region)     -   19 a first receiver (second region)     -   19 b second receiver (first region)     -   21 second compressor     -   33-36 third to sixth expansion valves     -   41-49 first to ninth on-off valves     -   50-57 tenth to seventeenth on-off valves     -   90 heat-load circuit     -   91 heat-load heat exchanger     -   92 pump

CITATION LIST Patent Literature

-   PTL 1: Japanese Unexamined Patent Application Publication No.     2015-197254 

1. A refrigeration cycle apparatus, wherein the refrigeration cycle apparatus performs a heating operation by performing a two-stage refrigeration cycle, the two-stage refrigeration cycle including a use-side refrigeration cycle using a first refrigerant having 1 MPa or less at 30° C. and a heat-source-side refrigeration cycle using a second refrigerant having 1.5 MPa or more at 30° C., and performs a cooling operation by performing a single-stage refrigeration cycle using the first refrigerant.
 2. The refrigeration cycle apparatus according to claim 1, comprising an outdoor heat exchanger that functions as an evaporator of the second refrigerant during the heating operation and functions as a radiator of the first refrigerant during the cooling operation.
 3. The refrigeration cycle apparatus according to claim 2, comprising a cascade heat exchanger including a first cascade flow path through which the first refrigerant flows during the heating operation and a second cascade flow path that is independent of the first cascade flow path and through which the second refrigerant flows during the heating operation, the cascade heat exchanger being configured to exchange heat between the first refrigerant and the second refrigerant.
 4. The refrigeration cycle apparatus according to claim 3, comprising a use heat exchanger in which the first refrigerant radiates heat during the heating operation, wherein during the heating operation, the first refrigerant evaporates when passing through the first cascade flow path, and the second refrigerant radiates heat when passing through the second cascade flow path.
 5. The refrigeration cycle apparatus according to claim 4, wherein the first refrigerant evaporates in the use heat exchanger during the cooling operation.
 6. The refrigeration cycle apparatus according to claim 2, wherein the first refrigerant is collectable in a first region other than the outdoor heat exchanger, and the second refrigerant is collectable in a second region other than the outdoor heat exchanger and other than the first region.
 7. A refrigeration cycle apparatus, wherein the refrigeration cycle apparatus performs a heating operation by performing a two-stage refrigeration cycle, the two-stage refrigeration cycle including a use-side refrigeration cycle using a first refrigerant having 1 MPa or less at 30° C. and a heat-source-side refrigeration cycle using a second refrigerant having 1.5 MPa or more at 30° C., and performs a cooling operation by performing a two-stage refrigeration cycle, the two-stage refrigeration cycle including a use-side refrigeration cycle using the second refrigerant and a heat-source-side refrigeration cycle using the first refrigerant.
 8. The refrigeration cycle apparatus according to claim 7, wherein a refrigerant to be used in the heat-source-side refrigeration cycle and a refrigerant to be used in the use-side refrigeration cycle are interchanged between the heating operation and the cooling operation.
 9. The refrigeration cycle apparatus according to claim 8, comprising a refrigerant tank that temporarily stores either the first refrigerant or the second refrigerant when the refrigerants are interchanged.
 10. The refrigeration cycle apparatus according to claim 7, comprising a cascade heat exchanger including a first cascade flow path in which the first refrigerant evaporates during the heating operation and a second cascade flow path that is independent of the first cascade flow path and in which the second refrigerant radiates heat during the heating operation, the cascade heat exchanger being configured to exchange heat between the first refrigerant and the second refrigerant.
 11. The refrigeration cycle apparatus according to claim 7, comprising a use heat exchanger that functions as a radiator of the first refrigerant during the heating operation and functions as an evaporator of the second refrigerant during the cooling operation.
 12. The refrigeration cycle apparatus according to claim 7, comprising an outdoor heat exchanger that functions as an evaporator of the second refrigerant during the heating operation and functions as a condenser of the first refrigerant during the cooling operation.
 13. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus detects a state of mixing of the first refrigerant and the second refrigerant.
 14. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus separates the first refrigerant and the second refrigerant from each other.
 15. The refrigeration cycle apparatus according to claim 1, wherein the first refrigerant includes at least one of R1234yf or R1234ze.
 16. The refrigeration cycle apparatus according to claim 1, wherein The second refrigerant includes carbon dioxide.
 17. The refrigeration cycle apparatus according to claim 3, wherein the first refrigerant is collectable in a first region other than the outdoor heat exchanger, and the second refrigerant is collectable in a second region other than the outdoor heat exchanger and other than the first region.
 18. The refrigeration cycle apparatus according to claim 4, wherein the first refrigerant is collectable in a first region other than the outdoor heat exchanger, and the second refrigerant is collectable in a second region other than the outdoor heat exchanger and other than the first region.
 19. The refrigeration cycle apparatus according to claim 5, wherein the first refrigerant is collectable in a first region other than the outdoor heat exchanger, and the second refrigerant is collectable in a second region other than the outdoor heat exchanger and other than the first region.
 20. The refrigeration cycle apparatus according to claim 8, comprising a cascade heat exchanger including a first cascade flow path in which the first refrigerant evaporates during the heating operation and a second cascade flow path that is independent of the first cascade flow path and in which the second refrigerant radiates heat during the heating operation, the cascade heat exchanger being configured to exchange heat between the first refrigerant and the second refrigerant. 